Transmission case, control valve, and transmission

Abstract

To suppress propagation of vibration to a control valve.MEANS FOR SOLVING THE PROBLEM: A transmission case has a support wall for a control valve and a pump. The support wall has a first region in which the control valve is mounted, and a second region in which the pump is mounted. The first region and the second region are aligned in a horizontal direction. A density of fastening points of the control valve on the support wall is higher in a region that overlaps with the pump when viewed from the horizontal direction than in the region that does not overlap with the pump.SELECTED DRAWING: Figure 4

Description

Technical Field

[0001] The present invention relates to a transmission case, a control valve, and a transmission.

Background Art

[0002] Patent Document 1 discloses a drive device for a vehicle.

Prior Art Document

Patent Document

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the case (transmission case) of this vehicle drive device (transmission), a hydraulic control device (control valve) is arranged in a standing posture. Further, in the case, the rotation shafts of an electric oil pump and a mechanical oil pump are arranged in a direction along the rotation shaft of the power transmission device. The electric oil pump and the mechanical oil pump are supported by the case while being arranged side by side in the direction of the rotation shaft of the power transmission device.

[0005] In the case, the hydraulic control device is also supported. When the electric oil pump and / or the mechanical oil pump is driven, vibration due to the drive may be transmitted to the hydraulic control device through the case and the hydraulic control device may vibrate. When the hydraulic control device vibrates, there is a possibility that a runout (oil runout) caused by the vibration occurs in the hydraulic pressure generated by the hydraulic control device (control valve). Therefore, it is required to suppress the vibration of the control valve.

Means for Solving the Problems

[0006] One aspect of the present invention is A transmission case having a support wall for a control valve and a pump, The aforementioned support wall is It has a first region to which the control valve is attached and a second region to which the pump is attached, The first and second regions are aligned in the horizontal direction. The transmission case has a density of fastening points for the control valve on the support wall such that the area overlapping the pump, when viewed from the horizontal direction, is higher than the area not overlapping the pump.

[0007] Other aspects of the present invention include: A control valve that is mounted together with the pump to the support wall of the transmission case, The control valve and the pump are arranged in the horizontal direction. The control valve is such that the density of fastening points to the support wall is higher in the region overlapping with the pump when viewed from the horizontal direction than in the region not overlapping with the pump.

[0008] Other aspects of the present invention include: A control valve that controls the hydraulic pressure supplied to the transmission mechanism, A pump that supplies oil to the control valve, A transmission comprising the control valve and a transmission case having a support wall for the pump, In the support wall, the control valve and the pump are aligned in the horizontal direction. The transmission has a higher density of fastening points of the control valve to the support wall in the region overlapping with the pump when viewed from the horizontal direction than in the region not overlapping with the pump. [Effects of the Invention]

[0009] According to one aspect of the present invention, vibrations of the control valve can be suppressed. [Brief explanation of the drawing]

[0010] [Figure 1] Figure 1 is a schematic diagram for explaining the arrangement of a power transmission device in a vehicle. [Figure 2] Figure 2 is a schematic diagram showing the schematic configuration of the power transmission device. [Figure 3] Figure 3 is a diagram for explaining the schematic configuration of a hydraulic control circuit. [Figure 4] Figure 4 is a schematic diagram of the case viewed from the third cover side. [Figure 5] Figure 5 is a diagram for explaining the bottom wall portion of the housing portion. [Figure 6] Figure 6 is a diagram for explaining the fastening point of the control valve and the electric oil pump. [Figure 7] Figure 7 is a diagram for explaining the mounting surface of the control valve. [Figure 8] Figure 8 is a diagram for explaining the arrangement of brackets for suppressing the vibration of the electric oil pump.

Embodiments for Carrying Out the Invention

[0011] First, the definitions of the terms in this specification will be explained. The power transmission device is a device having at least a power transmission mechanism, and the power transmission mechanism is, for example, at least one of a speed change mechanism, a gear mechanism, a differential gear mechanism, and a reduction mechanism. In the following embodiments, the case where the power transmission device 1 is a speed change gear for transmitting the output rotation of the engine will be exemplified. The power transmission device 1 may be any device that transmits the output rotation of at least one of the engine and the motor (rotary electric machine).

[0012] "Overlap in a predetermined direction view" means that a plurality of elements are arranged in a predetermined direction, and is synonymous with the case of being described as "overlap in a predetermined direction". The "predetermined direction" is, for example, the axial direction, the radial direction, the vertical line direction, the horizontal line direction, the vehicle traveling direction (vehicle forward direction, vehicle reverse direction), etc. When it is illustrated on the drawing that a plurality of elements (parts, components, etc.) are arranged in a predetermined direction, in the description of the specification, it may be regarded that there is a sentence explaining that they overlap in the view in the predetermined direction.

[0013] "Do not overlap in the view in the predetermined direction" and "offset in the view in the predetermined direction" mean that a plurality of elements are not arranged in the predetermined direction, and are synonymous with the case of describing "do not overlap in the predetermined direction" and "offset in the predetermined direction". The "predetermined direction" is, for example, the axial direction, the radial direction, the vertical line direction, the horizontal line direction, the vehicle traveling direction (vehicle forward direction, vehicle backward direction), etc. When it is illustrated on the drawing that a plurality of elements (parts, components, etc.) are not arranged in a predetermined direction, in the description of the specification, it may be regarded that there is a sentence explaining that they do not overlap in the view in the predetermined direction.

[0014] "In the view in the predetermined direction, the first element (part, component, etc.) is located between the second element (part, component, etc.) and the third element (part, component, etc.)" means that when observed from the predetermined direction, it can be observed that the first element is between the second element and the third element. The "predetermined direction" is the axial direction, the radial direction, the vertical line direction, the horizontal line direction, the vehicle traveling direction (vehicle forward direction, vehicle backward direction), etc. For example, when the second element, the first element, and the third element are arranged in this order along the axial direction, it can be said that in the view in the radial direction, the first element is located between the second element and the third element. When it is illustrated on the drawing that in the view in the predetermined direction, the first element is between the second element and the third element, in the description of the specification, it may be regarded that there is a sentence explaining that in the view in the predetermined direction, the first element is between the second element and the third element.

[0015] The "axial direction" means the axial direction of the rotation axis of the parts constituting the power transmission device. The "radial direction" means the direction perpendicular to the rotation axis of the parts constituting the power transmission device. The parts are, for example, a motor, a gear mechanism, a differential gear mechanism, etc.

[0016] "Vertical mounting" of a control valve means that, in the case of a control valve with a basic configuration in which valve bodies and separate plates are stacked alternately, the valve bodies of the control valve are stacked in a horizontal direction relative to the installation state of the power transmission unit on the vehicle. Here, "horizontal direction" does not mean a horizontal direction in the strict sense, but also includes cases where the stacking direction is inclined with respect to the horizontal line.

[0017] Furthermore, "vertical mounting" of the control valve means that the control valve is positioned such that the multiple operating valves (valve bodies) within the control valve are aligned in the vertical direction VL, based on the installation state of the power transmission system on the vehicle. "Arranging multiple operating valves in the direction of the vertical line VL" means that the operating valves within the control valve are positioned with their positions offset in the direction of the vertical line VL.

[0018] In this case, the multiple operating valves do not need to be strictly aligned in a straight line in the vertical direction VL. For example, when a control valve is formed by stacking multiple valve bodies, in a vertically oriented control valve, the multiple operating valves may be aligned in the vertical direction VL, with their positions shifted in the direction of the stacking of the valve bodies.

[0019] Furthermore, when viewed from the axial direction (direction of forward and backward movement) of the valve body of an operating valve, it is not necessary for all operating valves to be spaced apart in the vertical direction VL. When viewed from the axial direction (direction of forward and backward movement) of the valve bodies of the operating valves, it is not necessary for all operating valves to be adjacent to each other in the vertical direction VL.

[0020] Therefore, for example, if the operating valves arranged in the vertical direction VL are offset in the stacking direction (horizontal direction) of the valve bodies, this also includes cases where, when viewed from the stacking direction, adjacent operating valves in the vertical direction VL are positioned in a partially overlapping position.

[0021] Furthermore, if the control valve is "vertically mounted," it means that the multiple operating valves within the control valve are arranged so that the direction of movement of the valve bodies of those operating valves is aligned with the horizontal line. In this case, the direction of movement of the valve body is not limited to the horizontal direction in a strict sense. The direction of movement of the valve body may be along the rotation axis X of the power transmission device, in which case the direction of rotation axis X and the sliding direction of the valve body are the same. Furthermore, the direction of movement of the valve body is not limited to the direction along the rotation axis X of the power transmission device, but may be, for example, in a direction perpendicular to it.

[0022] Embodiments of the present invention will be described below. Figure 1 is a schematic diagram illustrating the arrangement of the power transmission device 1 in vehicle V. Figure 2 is a schematic diagram illustrating the general configuration of the power transmission device 1.

[0023] As shown in Figure 1, the power transmission device 1 is positioned between the left and right frames FR, FR at the front of the vehicle V. The housing HS of the power transmission device 1 consists of a case 6, a first cover 7, a second cover 8, and a third cover 9. As shown in Figure 2, the housing HS contains a torque converter T / C, a forward / reverse switching mechanism 2, a variator 3, a reduction mechanism 4, a differential 5, an electric oil pump EOP, a mechanical oil pump MOP, a control valve CV, and the like.

[0024] In the power transmission device 1, the output rotation of the engine ENG (drive source) is input to the forward / reverse switching mechanism 2 via the torque converter T / C. The rotation input to the forward / reverse switching mechanism 2 is input to the primary pulley 31 of the variator 3, either in forward or reverse direction.

[0025] In the variator 3, by changing the winding radius of the belt 30 on the primary pulley 31 and the secondary pulley 32, the rotation input to the primary pulley 31 is shifted to a desired gear ratio and output from the output shaft 33 of the secondary pulley 32.

[0026] The output rotation of the secondary pulley 32 is input to the differential gear 5 (differential gear mechanism) via the reduction mechanism 4, and then transmitted to the drive wheels WH, WH via the left and right drive shafts 55A, 55B. The reduction mechanism 4 includes an output gear 41, an idler gear 42, a reduction gear 43, and a final gear 45.

[0027] In the power transmission device 1, the forward / reverse switching mechanism 2, the torque converter T / C, and the output shaft of the engine ENG are arranged coaxially (concentrically) on the rotation axis X1 (first axis) of the primary pulley 31. The output shaft 33 of the secondary pulley 32 and the output gear 41 are arranged coaxially on the rotation axis X2 (second axis) of the secondary pulley 32. The idler gear 42 and the reduction gear 43 are arranged coaxially on a common rotation axis X3. The final gear 45 and the drive shafts 55A and 55B are arranged coaxially on a common rotation shaft X4. In the power transmission device 1, these rotation shafts X1 to X4 are set to be parallel to each other. Hereafter, these rotation shafts X1 to X4 will be collectively referred to as the rotation shaft X of the power transmission device 1 (power transmission mechanism) as needed.

[0028] As shown in Figure 2, case 6 has a partition wall 62. The partition wall 62 is provided in a range that crosses the rotation axes (rotation axes X1 to X4) of the power transmission mechanism. The partition wall 62 divides the inside of the case 6 into two sections in the direction of the rotation axis X1. One side of the partition wall 62 in the direction of the rotation axis X1 is the first chamber S1, and the other side is the third chamber S3.

[0029] The first chamber S1 houses the forward / reverse switching mechanism 2, the reduction mechanism 4, the differential 5, the mechanical oil pump MOP, and the strainer 10. The third chamber S3 houses the variator 3. In case 6, the opening on the first chamber S1 side is sealed with the second cover 8 (torque converter cover). The opening on the third chamber S3 side is sealed with the first cover 7 (side cover). In Case 6, oil used for operating the power transmission device 1 and for lubricating the components of the power transmission device 1 is stored in the lower part of the space between the first cover 7 and the second cover 8 (first chamber S1, third chamber S3).

[0030] In Case 6, a storage compartment 65 is attached to the front side of the vehicle. The storage compartment 65 is oriented along the rotation axis X of the power transmission device 1 (or oriented along the left-right direction in Figure 2). The storage compartment 65 has a bottom wall 66 and a surrounding wall 67. In the housing HS, the opening in the surrounding wall 67 is sealed with the third cover 9, thereby forming a closed storage chamber S2 (second chamber) on the side facing the front of the vehicle (see Figure 2). The control valve CV and the electric oil pump EOP are located inside the containment chamber S2.

[0031] The power transmission device 1 is equipped with one mechanical oil pump MOP and one electric oil pump EOP as oil pumps. These oil pumps draw in oil OL stored in the lower part of the housing HS through the strainer 10, pressurize the drawn oil OL, and supply it to the hydraulic control circuit 95 (see Figure 3) in the control valve CV. The hydraulic control circuit 95 supplies hydraulic pressure (operating hydraulic pressure) for driving the power transmission mechanism, as well as oil OL used for lubrication and cooling of the power transmission mechanism. The hydraulic control circuit 95 includes pressure regulating valves 97 (97a to 97b), control valves 98 (98a, 98b), and switching valves 99 related to regulating the hydraulic pressure (operating hydraulic pressure), and solenoids 96 (96a to 96d) that output signal pressure. In the following explanation, these will be collectively referred to as operating valves.

[0032] Figure 3 illustrates an example of a hydraulic control circuit 95 within a control valve CV. Figure 3 shows the configuration of the part of the hydraulic control circuit 95 that is involved in regulating the operating hydraulic pressure of the variator 3 (primary pulley 31, secondary pulley 32). In the following explanation, if there is no distinction between the mechanical oil pump (MOP) and the electric oil pump (EOP), they will also be referred to as the oil pump (OP).

[0033] As shown in Figure 3, the pressure regulating valve 97a (first pressure regulating valve) adjusts the line pressure from the hydraulic pressure generated by the oil pump OP by adjusting the amount of oil OL drained at the pressure regulating valve 97a. The line pressure adjusted by the pressure regulating valve 97a is supplied to the control valve 98a of the primary pulley 31, the control valve 98b of the secondary pulley 32, and the pressure regulating valve 97b (second pressure regulating valve).

[0034] The pressure regulating valve 97b adjusts the pilot pressure from the line pressure. Solenoids 96a (line pressure solenoid), 96b (primary solenoid), 96c (secondary solenoid), and 96d (select solenoid) each operate based on commands from a control device (not shown) to regulate the signal pressure from the pilot pressure and output it.

[0035] In control valves 98a and 98b, the valve body (not shown) housed inside moves in the axial direction (Xp direction in the figure) in response to the signal pressure. When the valve body moves in the direction of the axis Xp, the line pressure regulated by the pressure regulating valve 97a is adjusted to a pressure corresponding to the position of the valve body, and then supplied from the control valves 98a and 98b to the pressure receiving chambers of the corresponding pulleys (primary pulley 31, secondary pulley 32). The aforementioned pressure regulating valve 97a is located on the upstream side (oil pump OP side) of the hydraulic control circuit 95, and the hydraulic pressure generated by the oil pump OP is supplied to it first.

[0036] In the switching valve 99, the valve body (not shown) housed inside moves in the axial direction (Xp direction in the figure) by an actuator driven in response to the operator's operation. As the valve body moves from one direction along the axis Xp to the other, the hydraulic pressure supplied by the solenoid 96d is switched from the forward clutch (forward clutch) to the reverse clutch (reverse clutch) of the forward / reverse switching mechanism 2 (moving in the opposite direction switches from the reverse clutch to the forward clutch).

[0037] Figure 4 is a view of the storage compartment 65 from the front of the vehicle. In Figure 4, intersecting hatching is added to the joint 671 of the surrounding wall 67 to make its location easier to understand. Furthermore, in Figure 4, hatching is added to the bolts 15 (15a~15o) involved in fixing the control valve CV to the bottom wall 66 and the bolts 16 (16a~16d) involved in fixing the electric oil pump EOP to the bottom wall 66.

[0038] Figure 5 is a diagram illustrating the bottom wall portion 66 (first region 661, second region 662) of the housing portion 65. In Figure 5, intersecting hatching is added to the joint portion 671 of the surrounding wall 67 to make its location easier to understand. Furthermore, in Figure 5, intersecting hatching is added to the mounting portions 68, 69A, and 69B of the control valve CV to make their locations easier to understand. In addition, intersecting hatching is added to the bolt bosses 27A to 27D, which are the mounting portions of the electric oil pump EOP.

[0039] As shown in Figure 5, the housing section 65 has a bottom wall section 66 and a surrounding wall section 67. The bottom wall portion 66 of the housing portion 65 has a first region 661, which is approximately half the size of the engine ENG side, and is integrated with the peripheral wall portion 61 of the case 6 (see Figure 2). The second region 662, which is approximately half the size of the opposite side, is provided on an extension of the first region 661, with a gap between it and the outer circumference of the first cover 7 (see Figure 2). In Figure 2, the area where the first region 661 and the peripheral wall portion 61 are integrated is shown with intersecting hatching.

[0040] As shown in Figure 4, the surrounding wall 67 encloses the entire outer circumference of the bottom wall portion 66. The housing portion 65 is formed in a closed-bottom cylindrical shape with the opening of the surrounding wall 67 facing the front of the vehicle. The end face of the surrounding wall 67 on the near side of the paper forms a joint 671 with the third cover 9. The joint 671 is a flange-like portion that surrounds the opening on the third cover 9 side of the surrounding wall 67 all around.

[0041] When viewed from the front of the vehicle, the storage compartment S2 is formed with a range in the direction of the rotation axis X1 (left-right direction in the figure) that extends from the area overlapping with case 6 to the area overlapping with the first cover 7. As shown in Figures 4 and 5, in the bottom wall portion 66, the control valve CV is installed in the first region 661, which overlaps with the case 6. The electric oil pump EOP is installed in the lower part of the second region 662, which overlaps with the first cover 7. Within the containment chamber S2, the control valve CV and the electric oil pump EOP are aligned in a direction along the rotation axis X of the power transmission device 1 (power transmission mechanism) (left-right direction in the diagram).

[0042] As shown in Figure 2, the control valve CV has a basic configuration in which the valve body 921 and the separate plate 920 are stacked alternately. Inside the containment chamber S2, the control valve CV is positioned vertically with the stacking direction of the valve bodies 921, 921 aligned with the vehicle's longitudinal direction (up and down direction in the diagram). As shown in Figure 4, in the housing chamber S2, the control valve CV is mounted vertically such that the following conditions are met: (a) The valve bodies of the pressure regulating valve 97 (97a~97b), the control valve 98 (98a, 98b), the switching valve 99, and the valve body driven by the solenoid 96 (96a~96d) of the control valve CV are aligned in the vertical direction VL (up and down direction) with respect to the installation state of the power transmission device 1 on the vehicle V; (b) The direction of advancement and retraction of the valve bodies (not shown) of the pressure regulating valve 97, the control valve 98, and the switching valve 99 (axis Xp direction) and the direction of advancement and retraction of the valve body driven by the solenoid 96 (axis Xp direction) are aligned with the horizontal direction. In other words, the valves are arranged in the direction of the vertical line VL, with the direction of movement of the valve body of each valve aligned with the horizontal line.

[0043] By aligning the direction of the valve body's reciprocating movement (axis Xp direction) with the horizontal line, the valve body's reciprocating movement is less obstructed compared to the case where the direction of the valve body's reciprocating movement is significantly inclined with respect to the horizontal line. Furthermore, by arranging the control valve CV vertically so that the pressure regulating valve 97, control valve 98, switching valve 99, and solenoid 96 are aligned in the vertical line VL direction, the housing chamber S2 that accommodates the control valve CV does not need to be enlarged in the longitudinal direction of the vehicle.

[0044] Figure 6 is a schematic diagram of the control valve CV and electric oil pump EOP housed in the housing chamber S2, as seen from the front of the vehicle. In Figure 6, the area of ​​the notch 923 and the bolts 15 (15a~15o) involved in fixing the control valve CV to the case 6 (bottom wall portion 66) and the bolts 16 (16a~16d) involved in fixing the electric oil pump EOP to the case 6 (bottom wall portion 66) are shown with intersecting hatching.

[0045] As shown in Figure 6, when viewed from the front of the vehicle, the control valve CV has a roughly L-shape, with a rectangular valve body 921 having a notch 923. In Figure 6, the area of ​​the notch 923 is indicated by intersecting hatching. In the containment chamber S2, the notch 923 is located on the lower side of the area that overlaps with the first cover 7 (see Figure 4). When viewed from the front of the vehicle, at least a portion of the electric oil pump (EOP) is housed in the notch 923.

[0046] As shown in Figure 4, the electric oil pump EOP has a basic configuration in which a control unit 931, a motor unit 932, and a pump unit 933 are arranged in series in the direction of the motor's rotation axis Z1. The electric oil pump EOP is positioned with its rotating shaft Z1 perpendicular to the rotating shaft X of the power transmission device 1. In this configuration, the rotating shaft Z1 of the electric oil pump EOP is oriented along the vertical line VL (up and down direction). Furthermore, the pump section 933 of the electric oil pump EOP is positioned at the lowest part of the housing chamber S2. The electric oil pump (EOP) is fixed to the second region 662 of the bottom wall 66 by four bolts 16 (16a to 16d). Specifically, it is fixed to the mounting region 663 (see Figure 5) at the bottom of the second region 662.

[0047] As shown in Figure 6, the upper part of the control valve CV extends above the electric oil pump EOP. When viewed from the vertical VL direction (the direction of the rotation axis Z1 of the electric oil pump EOP), the electric oil pump EOP is positioned in a position that overlaps with the control valve CV. In the control valve CV, when viewed from the direction of the vertical line VL, the area to the right of the vertical line VL1 passing through the base end of the notch 923 is the overhang region Rw with the electric oil pump EOP.

[0048] In this embodiment, when arranging the electric oil pump EOP in the housing chamber S2, the control valve CV and the electric oil pump EOP are not simply placed in parallel, but rather the electric oil pump EOP is positioned using the notch 923 provided in the control valve CV. Therefore, compared to simply arranging the control valve CV and the electric oil pump EOP in the direction of the rotation axis X of the power transmission mechanism, the width of the housing chamber S2 (in the vehicle width direction) is shortened by the amount of the notch 923.

[0049] The hydraulic control circuit 95 inside the control valve CV adjusts the operating hydraulic pressure of the power transmission mechanism (forward / reverse switching mechanism 2, variator 3, etc.) from the hydraulic pressure generated by the oil pump. When the electric oil pump EOP is driven, vibrations are generated due to the operation of the pump unit 933. If the electric oil pump EOP and the control valve CV are supported by a common support wall, the vibrations generated in the electric oil pump EOP may be transmitted to the control valve CV via the bottom wall 66. If the control valve CV vibrates due to transmitted vibrations, the hydraulic pressure (operating hydraulic pressure) output from the control valve CV may fluctuate due to the vibration, potentially causing what is known as oil vibration. In such cases, the operation of the power transmission mechanism (e.g., variator 3) driven by the operating hydraulic pressure may be affected.

[0050] The vibrations of the electric oil pump EOP act on the bottom wall 66 from the fastening points Ta to Td by bolts 16 (16a to 16d). The electric oil pump EOP is located on the lower side of the bottom wall portion 66. In this embodiment, the total number of fastening points Pa to Po of the control valve CV by bolts 15 (15a to 15o) located on the lower side where the electric oil pump EOP is located is greater than the total number of fastening points located on the upper side, and the density of fastening points in the lower region is set to be higher than the density of fastening points in the upper region.

[0051] in particular, (A) The distribution of fastening points of the control valve CV is such that there are many fastening points on the sides of fastening points Ta to Td by bolts 16a to 16d of the electric oil pump EOP, and the density of fastening points on the sides of fastening points Ta to Td is higher than the density of fastening points in the region outside the sides of fastening points Ta to Td.

[0052] As shown in Figure 6, in this embodiment, the fastening points Ph and Pi of the control valve CV are set along the straight line HL1 passing through the fastening points Ta and Tc of the electric oil pump EOP, and the fastening points Pj, Pk, and Pl of the control valve CV are set along the straight line HL2 passing through the fastening points Tb and Td of the electric oil pump EOP. Furthermore, the total number of fastening points (Ph~Po) in the region R1 below the straight line HL1 (8 locations) is greater than the total number of fastening points (Pa~Pg) in the region R1' above the straight line HL1 (7 locations).

[0053] As shown in Figure 6, in this embodiment, the height ratio between the region R1 below the line HL1 and the region R1' above the line HL1 is approximately 1:2. Consequently, the total number of fastening points (Ph~Po) in the region R1 below the straight line HL1 (8 locations) is greater than the total number of fastening points (Pa~Pg) in the region R1' above the straight line HL1 (7 locations). Therefore, the density of fastening points (Ph~Po) in the region R1 below the straight line HL1 is higher than the density of fastening points (Pa~Pg) in the region R1' above the straight line HL1.

[0054] As shown in Figure 6, in Case 6, the region between the straight line HL1 and the straight line HL2 can be said to be the region where vibrations from the electric oil pump EOP are concentrated and propagated. Therefore, by increasing the number of fastening points of the control valve CV in region R1, at least below the straight line HL1, and increasing the density of fastening points, the support strength of the control valve CV in the region where vibrations concentrate and propagate can be increased. This suppresses vibrations of the control valve CV caused by the propagation of vibrations from the electric oil pump EOP.

[0055] (B) In addition to the configuration of (A) above, multiple fastening points (Ph, Pi) are arranged along the straight line HL1, and multiple fastening points (Pj, Pk, Pl) are arranged along the straight line HL2. The fastening points Pi and Pl of the control valve CV are positioned close to the fastening points Ta and Tb of the electric oil pump EOP.

[0056] As shown in Figure 6, by positioning the fastening points Pi and Pl of the control valve CV close to the fastening points Ta and Tb of the electric oil pump EOP, vibrations of the control valve CV near the point where vibrations of the electric oil pump EOP act on the case 6 can be more reliably suppressed. Furthermore, vibrations propagating along the straight lines HL1 and HL2 can be suppressed by the fastening points Ph, Pi, Pj, Pk, and Pl, which cause vibrations in the control valve CV.

[0057] (C) In addition to at least one of the above configurations (A) and (B), a plurality of operating valves (pressure regulating valve, control valve, switching valve and solenoid) are arranged at intervals in the vertical direction VL (up and down direction in Figure 6) with reference to the installation state of the power transmission device 1 on the vehicle V. Then, a fastening point (Ph~Po) is set between the operating valves arranged in the vertical direction VL.

[0058] As shown in Figure 6, in the control valve CV, the solenoids 96 (96a to 96d) are arranged with vertical spacing between them in the front layer (the layer closest to the viewer) of the vehicle V. Furthermore, although not shown in the illustration, in the layer at the back of the page of the control valve CV, pressure regulating valves 97 (97a-97b), control valves 98 (98a, 98b), and switching valves 99 are arranged with gaps in the vertical direction. In this embodiment, the arrangement of fastening points along the straight line HL1 and the arrangement of fastening points along the straight line HL2 are positioned between adjacent operating valves in the vertical direction. Note that in Figure 6, only the solenoids 96a, 96b, and 96c in the layer on the front side of the control valve CV are visible, so here we will explain the case where the operating valve is a solenoid.

[0059] Furthermore, the solenoid 96a is positioned between the arrangement of fastening points along the straight line HL2 and the arrangement of fastening points along the straight line HL4. In the control valve CV, the thickness of the area where the solenoid 96 is located is greater than other areas by the thickness of the valve body (not shown) driven by the solenoid 96. Therefore, in the control valve CV, the region where the valve body of the solenoid 96 is located has higher rigidity than other regions, making it less susceptible to the effects of vibrations transmitted from the electric oil pump EOP. Therefore, with the above configuration, the region of the valve body of the highly rigid solenoid 96 and the arrangement of fastening points are alternately arranged in the vertical direction VL (up and down direction) with reference to the installation state of the power transmission device 1 on the vehicle V. This increases the rigidity of the control valve CV and enhances the support of the control valve CV against the bottom wall portion 66, thereby suppressing the transmission of vibrations to the control valve CV.

[0060] The explanation was given in terms of the positional relationship between the solenoid 96 and the fastening point. The fastening point is located in a position that avoids interference with the pressure regulating valve 97 (97a to 97b), the control valve 98 (98a, 98b), and the switching valve 99.

[0061] (D) In ​​addition to at least one of the above configurations (A), (B), and (C), a fastening point Pg is set in the overhang region Rw of the control valve CV. When viewed from the vertical line VL direction, the fastening point Ta of the electric oil pump EOP and the fastening point Pg of the control valve CV are positioned in close proximity to each other.

[0062] As shown in Figure 6, by setting the fastening point Pg in the overhang region Rw, it is possible to suppress vibrations of the control valve CV caused by vibrations propagating from the fastening point Ta along the vertical line VL.

[0063] (E) In addition to at least one of the above configurations (A), (B), (C), and (D), The fastening points Pd and Pe of the control valve CV are set along the straight line HL5 that runs along the upper edge of the notch 923 of the control valve CV.

[0064] As shown in Figure 6, the control valve CV changes in size in the vehicle width direction at the upper edge of the notch 923. When vibrations are transmitted to the control valve CV, stress caused by the vibrations may concentrate at the part where the size in the vehicle width direction changes. As described above, by setting fastening points Pd and Pe along the straight line HL5, the support strength of areas where stress may concentrate can be increased, thereby suppressing the effect of vibrations from the electric oil pump EOP on the control valve CV.

[0065] Thus, in the control valve CV, the total number of fastening points Pd to Po (12 locations) using bolts 15d to 15o within the region overlapping with the notch 923 where the electric oil pump EOP is located (region R3 in the figure), when viewed from the vehicle width direction (left-right direction in Figure 6) along the rotation axis X of the power transmission device 1, is greater than the total number of fastening points Pa to Pc (3 locations) using bolts 15a to 15c within the region that does not overlap (region R3' in the figure).

[0066] As shown in Figure 6, in this embodiment, the height ratio between the region R3 below the line HL5 and the region R3' above the line HL5 is approximately 1:0.6. Consequently, the total number of fastening points (Pd~Po) in the region R3 below the straight line HL5 (12 locations) is greater than the total number of fastening points (Pa~Pc) in the region R3' above the straight line HL5 (3 locations). Therefore, the density of fastening points (Pd~Po) in the region R3 below the straight line HL5 is higher than the density of fastening points (Pa~Pc) in the region R3' above the straight line HL5.

[0067] Furthermore, the total number of fastening points Pf to Po (10 locations) using bolts 15f to 15o within the region overlapping with the electric oil pump EOP (region R2 in the figure) was set to be greater than the total number of fastening points Pa to Pe (5 locations) using bolts 15a to 15e within the region not overlapping with the EOP (region R2' in the figure).

[0068] As shown in Figure 6, in this embodiment, the height ratio between the region R2 below the line HL3 and the region R2' above the line HL3 is approximately 1:0.9. Consequently, the total number of fastening points (Pf~Po) in the region R2 below the straight line HL3 (10 locations) is greater than the total number of fastening points (Pa~Pe) in the region R2' above the straight line HL3 (5 locations). Therefore, the density of fastening points (Pf~Po) in the region R2 below the straight line HL3 is higher than the density of fastening points (Pa~Pe) in the region R2' above the straight line HL3.

[0069] Furthermore, more preferably, the total number of fastening points Ph to Po (8 locations) using bolts 15h to 15o in the region below the straight line HL1 (region R1 in the figure), which overlaps with the electric oil pump EOP and passes through a point where the vibration of the electric oil pump EOP directly acts, is greater than the total number of fastening points Pa to Pg (7 locations) using bolts 15a to 15g in the region above the straight line HL1 (region R1' in the figure).

[0070] As shown in Figure 6, in this embodiment, the height ratio between the region R1 below the line HL1 and the region R1' above the line HL1 is approximately 1:2. Consequently, the total number of fastening points (Ph~Po) in the region R1 below the straight line HL1 (8 locations) is greater than the total number of fastening points (Pa~Pg) in the region R1' above the straight line HL1 (7 locations). Therefore, the density of fastening points (Ph~Po) in the region R1 below the straight line HL1 is higher than the density of fastening points (Pa~Pg) in the region R1' above the straight line HL1.

[0071] By setting the distribution and density of the fastening points of the control valve CV based on the positions where vibrations from the electric oil pump EOP are input to the bottom wall portion 66, the propagation of vibrations from the electric oil pump EOP to the control valve CV can be effectively suppressed.

[0072] To achieve this distribution and density of fastening points for the control valve CV, the bottom wall portion 66 of case 6 is configured with bolts 15a to 15o and bolt holes 27a to 27d into which bolts 16a to 16d are screwed. The distribution of bolt holes in the bottom wall portion 66 is described below.

[0073] As shown in Figure 5, a mounting area 663 for the electric oil pump EOP is provided at the lower part of the second area 662. When viewed from the front of the vehicle, the mounting area 663 is formed to be large enough to accommodate the electric oil pump EOP. Bolt bosses 27 (27A to 27D) are provided within the mounting area 663. On the first region 661 side of the mounting region 663 (left side in the figure), two bolt bosses 27A and 27B are provided spaced apart in the direction of the vertical line VL. On the opposite side from the first region 661 (right side in the figure), two bolt bosses 27C and 27D are provided spaced apart in the direction of the vertical line VL. Bolt holes 27a to 27d are provided in each of the bolt bosses 27 (27A to 27D).

[0074] The bolt bosses 27A and 27B on the left side of the diagram, and the bolt bosses 27C and 27D on the right side of the diagram, are positioned symmetrically with the rotating shaft Z1 of the electric oil pump EOP in between. The two bolt bosses 27A and 27C are located on a straight line HL1 passing through the centers of the bolt holes 27a and 27c. The two bolt bosses 27B and 27D are located on a straight line HL2 passing through the centers of the bolt holes 27b and 27d.

[0075] The end faces of the bolt bosses 27 (27A~27D) on the near side of the paper are flat surfaces located on the same plane. These end faces are the mounting surfaces for the electric oil pump EOP. Bolts 16a~16d (see Figure 4), which pass through the electric oil pump EOP, are screwed into (fixed) the bolt holes 27a~27d.

[0076] A connection port 28a is open between bolt boss 27B and bolt boss 27D. The connection port 28a is a connection port to an oil passage (not shown) provided inside the case 6. The connection port 28a is provided adjacent to bolt boss 27B. A connection port 28b is open between bolt boss 27C and bolt boss 27D. The connection port 28b is a connection port 28b to another oil passage (not shown) provided inside the case 6. The connection port 28b is provided in close proximity to bolt boss 27C.

[0077] Oil OL, discharged from the electric oil pump EOP and directed towards the control valve CV, is supplied to the connection port 28a. Oil OL is supplied from connection port 28b, drawn in via strainer 10 (see Figure 2), and directed toward the electric oil pump EOP. Thus, in the housing section 65, bolt bosses 27 (27A to 27D) related to the mounting of the electric oil pump EOP are provided in the mounting area 663 at the lower part of the second area 662.

[0078] As shown in Figure 5, the first region 661 is provided with mounting portions 68, 69A, and 69B. The mounting portions 68, 69A, and 69B protrude from the first region 661 toward the front of the paper. The mounting portion 68 is formed in the area from the lower to the upper part within the first region 661. Mounting parts 69A and 69B are located above mounting part 68. Mounting parts 69A and 69B are offset from each other in the direction of the rotation axis X (left-right direction in the figure) and in the direction of the vertical line VL. Mounting part 69B is located above mounting part 69A in the direction of the vertical line VL and is on the side of the second region 662 (right side in the figure).

[0079] The end faces 681, 691, and 691 of the mounting portions 68, 69A, and 69B on the near side of the paper are flat surfaces located on the same plane. These end faces 681, 691, and 691 are the mounting surfaces on the control valve CV side. Mounting sections 69A and 69B are each provided with bolt holes 25 (25a and 25b). Bolts 15a and 15b (see Figure 4), which pass through the control valve CV, are screwed into bolt holes 25a and 25b. The mounting portion 68 is provided with multiple bolt holes 25 (25c to 25o). Bolts 15a to 15o, used for attaching the control valve CV to the bottom wall portion 66, are screwed into the bolt holes 25 (25a to 25o). The centers of the bolt holes 25 (25a to 25o) correspond to the fastening points Pa to Po of the aforementioned bolts 15a to 15o.

[0080] The bolt hole 25c is located below the aforementioned bolt hole 25a. The bolt holes 25d and 25e are located below the bolt hole 25c, along the straight line HL5. The straight line HL5 is a straight line along the upper edge of the notch 923 (see Figure 3) of the control valve CV. The straight line HL5 is parallel to the straight lines HL1 and HL2 described above. The straight line HL5 is located above the straight lines HL1 and HL2 in the vertical line VL direction, with reference to the installation state of the power transmission device 1 on the vehicle.

[0081] Bolt hole 25e is located on the second region 662 side (right side in the diagram) compared to bolt holes 25c and 25d. In the direction of the vertical line VL, bolt hole 25e is located slightly above bolt hole 25d and intersects the line HL5. Bolt hole 25d is located slightly below the line HL5.

[0082] Bolt holes 25f and 25g are located below bolt hole 25e and along the straight line HL3. Bolt holes 25f and 25g are located below the straight line HL3 and are positioned close to the straight line HL3. Line HL3 is a straight line along the upper end of the electric oil pump EOP (see Figure 3). Line HL3 is parallel to the aforementioned lines HL1, HL2, and HL5. Line HL3 is located between line HL5 and line HL1 in the vertical direction VL, relative to the installation state of the power transmission device 1 on the vehicle.

[0083] Bolt hole 25g is located on the second region 662 side (right side in the figure) than bolt holes 25e and 25f. Bolt hole 25g is located in the overhang region Rw described later for the control valve CV. Bolt hole 25g is located on the second region 662 side (right side in the figure) than the vertical line VL1 passing through the base end of the overhang region Rw. Therefore, when viewed from the vertical VL direction, bolt hole 25g is located in a position that overlaps with the electric oil pump EOP.

[0084] Bolt holes 25h and 25i are located below bolt hole 25f and along the straight line HL1. Bolt holes 25h and 25i are located below the straight line HL1 and are positioned close to the straight line HL1. The area surrounding the bolt hole 25i on the end face 681 is connected to the bolt boss 27A described above. In the connection area between the mounting portion 68 and the bolt boss 27A, the bolt hole 25i, which is involved in fixing the control valve CV, and the bolt hole 27a, which is involved in fixing the electric oil pump EOP, are adjacent to each other.

[0085] Bolt holes 25j, 25k, and 25l are located below bolt hole 25i and along the straight line HL2. Bolt holes 25j, 25k, and 25l are positioned in close proximity to the straight line HL2. The area surrounding the bolt hole 25l on the end face 681 is connected to the bolt boss 27B described above. In the connection area between the mounting portion 68 and the bolt boss 27B, the bolt hole 25l, which is involved in fixing the control valve CV, and the bolt hole 27b, which is involved in fixing the electric oil pump EOP, are adjacent.

[0086] Bolt holes 25m, 25n, and 25o are located below bolt hole 25l and along the straight line HL4. Bolt holes 25m, 25n, and 25o are located above the straight line HL4 and are positioned close to the straight line HL4. Line HL4 is a straight line that runs along the lower end of the electric oil pump EOP (see Figure 4). Line HL4 is parallel to the aforementioned lines HL1, HL2, HL3, and HL5.

[0087] Furthermore, in addition to the bolt holes 25c to 25o mentioned above, grooves 682 and holes 683 are formed on the end face 681 of the mounting portion 68. These grooves 682 and holes 683 form an oil passage between the control valve CV and the control valve CV after it has been installed.

[0088] Here, when the electric oil pump EOP is driven, vibrations caused by the operation of the electric oil pump EOP are transmitted from the bolt bosses 27 (27A~27D) to the case 6 (bottom wall 66 of the housing 65). If the control valve CV vibrates due to the vibrations transmitted to the case 6, it may affect the operating hydraulic pressure that the control valve CV regulates.

[0089] In this embodiment, the distribution and density of bolt holes 25 (25a~25o) in the bottom wall portion 66 of the case 6 are designed to reduce the extent to which vibrations transmitted from the electric oil pump EOP to the case 6 affect the control valve CV. Vibrations from the electric oil pump EOP are transmitted to the case 6 (bottom wall portion 66) from the fastening points Ta~Td (see Figure 6) of the electric oil pump EOP. Therefore, in the first region 661 where the control valve CV is installed, the distribution of bolt holes 25 (25a~25o) is set such that there are more bolt holes on the lower side, which is closer to the mounting region 663 of the electric oil pump EOP, than on the upper side, which is further away from the mounting region 663, and the density of bolt holes in the lower region is higher than the density of bolt holes in the upper region.

[0090] in particular, (A) The distribution of bolt holes related to the mounting of the control valve CV is large on the side of the bolt boss 27 (27A~27D) related to the mounting of the electric oil pump EOP, and the density of bolt holes on the side of the bolt boss 27 (27A~27D) is higher than in the area outside the side of the bolt boss 27 (27A~27D).

[0091] As shown in Figure 5, in this embodiment, bolt holes 25h and 25i for mounting the control valve CV are arranged along a straight line HL1 passing through bolt holes 27a and 27c for mounting the electric oil pump EOP, and bolt holes 25j, 25k, and 25l for mounting the control valve CV are arranged along a straight line HL2 passing through bolt holes 27b and 27d for mounting the electric oil pump EOP. Furthermore, the total number of bolt holes 25h to 25o (8 locations) in the region R1 below the straight line HL1 is greater than the total number of bolt holes 25a to 25g (7 locations) in the region R1' above the straight line HL1.

[0092] As shown in Figure 5, in this embodiment, the height ratio between the region R1 below the straight line HL1 and the region R1' above the straight line HL1 is approximately 1:2. Consequently, the total number of bolt holes 25h to 25o (8 locations) in region R1 below the straight line HL1 is greater than the total number of bolt holes 25a to 25g (7 locations) in region R1' above the straight line HL1. Therefore, the density of bolt holes 25h to 25o in region R1 below the straight line HL1 is higher than the density of bolt holes 25a to 25g in region R1' above the straight line HL1.

[0093] (B) In addition to (A) above, multiple bolt holes 25h and 25i are arranged along the straight line HL1, and multiple bolt holes 25j, 25k and 25l are arranged along the straight line HL2. The bolt holes 25i and 25l for mounting the control valve CV are positioned close to the bolt bosses 27A and 27B (bolt holes 27a and 27b) for mounting the electric oil pump EOP.

[0094] (C) In addition to at least one of the configurations of (A) and (B) above, the positions of bolt holes 25h, 25i and bolt holes 25j, 25k, 25l are set such that the bolt holes 25h, 25i and bolt holes 25j, 25k, 25l are arranged between a plurality of operating valves (pressure regulating valve, control valve, switching valve, and solenoid) in the vertical direction VL (up and down direction in Figure 6) with respect to the installation state of the power transmission device 1 on the vehicle V.

[0095] (D) In ​​addition to at least one of the above configurations (A), (B), and (C), the position of the bolt hole 25g is set such that the bolt hole 25g is located in the overhang region Rw of the control valve CV when viewed from the front of the vehicle. When viewed from the vertical line VL direction, the positions of bolt holes 27a and 25g are set so that the position of bolt hole 27a related to the mounting of the electric oil pump EOP and the position of bolt hole 25g related to the mounting of the control valve CV are close together.

[0096] (E) In addition to at least one of the above configurations (A), (B), (C), and (D), Bolt holes 25d and 25e for mounting the control valve CV are set along a straight line HL5 that runs along the upper edge of the notch 923 of the control valve CV.

[0097] Thus, in the control valve CV, the total number of bolt holes 25d to 25o (12 locations) in the area overlapping with the notch 923 where the electric oil pump EOP is located (area R3 in the figure), when viewed from the vehicle width direction (left-right direction in Figure 5) along the rotation axis X of the power transmission device 1, is greater than the total number of bolt holes 25a to 25c (3 locations) in the area not overlapping (area R3' in the figure).

[0098] As shown in Figure 5, in this embodiment, the height ratio between the region R3 below the line HL5 and the region R3' above the line HL5 is approximately 1:0.6. As a result, the total number of bolt holes 25d~25o (12 locations) in the region R3 below the straight line HL5 is greater than the total number of bolt holes 25a~25c (3 locations) in the region R3' above the straight line HL5. Therefore, the density of bolt holes 25d~25o in the region R3 below the straight line HL5 is higher than the density of bolt holes 25a~25c in the region R3' above the straight line HL5.

[0099] Furthermore, the total number of bolt holes 25f to 25o (10 locations) within the area overlapping with the electric oil pump EOP (area R2 in the diagram) was set to be greater than the total number of bolt holes 25a to 25e (5 locations) within the area not overlapping with the EOP (area R2' in the diagram).

[0100] As shown in Figure 5, in this embodiment, the height ratio between the region R2 below the line HL3 and the region R2' above the line HL3 is approximately 1:0.9. Consequently, the total number of bolt holes 25f~25o (10 locations) in the region R2 below the straight line HL3 is greater than the total number of bolt holes 25a~25e (5 locations) in the region R2' above the straight line HL3. Therefore, the density of bolt holes 25f~25o in the region R2 below the straight line HL3 is higher than the density of fastening points (Pa~Pe) in the region R2' above the straight line HL3.

[0101] Furthermore, more preferably, the total number of bolt holes 25h to 25o (8 locations) in the region below the straight line HL1 that passes through the point where the vibration of the electric oil pump EOP directly acts (region R1 in the figure) is greater than the total number of bolt holes 25a to 25g (7 locations) in the region above the straight line HL1 (region R1' in the figure).

[0102] As shown in Figure 5, in this embodiment, the height ratio between the region R1 below the straight line HL1 and the region R1' above the straight line HL1 is approximately 1:2. As a result, the total number of bolt holes 25h~25o (8 locations) in region R1 below the straight line HL1 is greater than the total number of bolt holes 25a~25g (7 locations) in region R1' above the straight line HL1. Therefore, the density of bolt holes 25h~25o in region R1 below the straight line HL1 is higher than the density of bolt holes 25a~25g in region R1' above the straight line HL1.

[0103] By setting the distribution and density of bolt holes involved in the mounting of the control valve CV in this way, the transmission of vibrations from the electric oil pump EOP to the control valve CV can be effectively suppressed.

[0104] Figure 7 is a schematic diagram showing the control valve CV and electric oil pump EOP housed in the containment chamber S2, as viewed from the rear of the vehicle. In Figure 7, intersecting hatching is used to indicate the area of ​​the separate plate 920, which is the mounting surface of the control valve CV to the case 6 (bottom wall portion 66). Furthermore, the through-holes 14 (14a~14o) of the control valve CV and the through-holes 18 (18a~18d) of the electric oil pump EOP are indicated by thick lines. Through holes 14 (14a to 14o) are through holes through which bolts 15 (15a to 15o) pass for fixing the control valve CV to the case 6 (bottom wall portion 66). Through holes 18 (18a to 18d) are through holes through which bolts 16 (16a to 16d) pass for fixing the electric oil pump EOP to the case 6 (bottom wall portion 66). The centers of the through holes 14 (14a to 14o) correspond to the fastening points Pa to Po of the bolts 15a to 15o mentioned above.

[0105] In order to achieve the aforementioned distribution of fastening points of the control valve CV, through holes 14 (14a to 14o) for bolts 15a to 15o are opened in the portion of the control valve CV facing the bottom wall portion 66.

[0106] in particular, (A) The distribution of through holes 14 related to the mounting of the control valve CV is large on the side of the fastening points Ta to Td (through holes 18a to 18d) of the electric oil pump EOP, and the density of through holes 14 (14a to 14o) on the side of the fastening points Ta to Td (through holes 18a to 18d) is higher than in the region outside the side of the fastening points Ta to Td. As shown in Figure 7, in this embodiment, through holes 14h and 14i of the control valve CV are arranged along a straight line HL1 passing through fastening points Ta and Tc (through holes 18a and 18c) related to the mounting of the electric oil pump EOP, and through holes 14j, 14k, and 14l related to the mounting of the control valve CV are arranged along a straight line HL2 passing through fastening points Tb and Td (through holes 18b and 18d) related to the mounting of the electric oil pump EOP. Furthermore, the total number of through holes 14h to 14o (8 locations) in the region R1 below the straight line HL1 is greater than the total number of through holes 14a to 14g (7 locations) in the region R1' above the straight line HL1.

[0107] As shown in Figure 7, in this embodiment, the height ratio between the region R1 below the straight line HL1 and the region R1' above the straight line HL1 is approximately 1:2. Consequently, the total number of through holes 14h to 14o (8 locations) in region R1 below the straight line HL1 is greater than the total number of through holes 14a to 14g (7 locations) in region R1' above the straight line HL1. Therefore, the density of through holes 14h to 14o in region R1 below the straight line HL1 is higher than the density of through holes 14a to 14g in region R1' above the straight line HL1.

[0108] (B) In addition to (A) above, through holes 14h and 14i are arranged along the straight line HL1, and multiple through holes 14j, 14k, and 14l are arranged along the straight line HL2. The through holes 14i and 14l are positioned close to the fastening points Ta and Tb (through holes 18a and 18b) related to the mounting of the electric oil pump EOP.

[0109] (C) In addition to the configuration of at least one of (A) and (B) above, the positions of the through holes 14h and 14i and the through holes 14j, 14k, and 14l are set so that the through holes 14h and 14i and the through holes 14j, 14k, and 14l are arranged between a plurality of operating valves (pressure regulating valve, control valve, switching valve, and solenoid) that are aligned in the vertical direction VL (up and down direction in Figure 6) with respect to the installation state of the power transmission device 1 on the vehicle V.

[0110] (D) In ​​addition to at least one of the above configurations (A), (B), and (C), the position of the through-hole 14g is set such that the through-hole 14g is located in the overhang region Rw of the control valve CV. The position of the through-hole 14 is set such that, when viewed from the vertical line VL direction, the fastening point Ta related to the mounting of the electric oil pump EOP and the through-hole 14g of the control valve CV are in close proximity.

[0111] (E) In addition to at least one of the above configurations (A), (B), (C), and (D), Through holes 14d and 14e are set along the straight line HL5 that runs along the upper edge of the notch 923 of the control valve CV.

[0112] Thus, in the control valve CV, the total number of through holes 14d to 14o (12 locations) in the region overlapping with the notch 923 where the electric oil pump EOP is located (region R3 in the figure), when viewed from the vehicle width direction (left-right direction in Figure 5) along the rotation axis X of the power transmission device 1, is greater than the total number of through holes 14a to 14c (3 locations) in the region that does not overlap (region R3' in the figure).

[0113] Thus, as shown in Figure 7, in this embodiment, the height ratio between the region R3 below the line HL5 and the region R3' above the line HL5 is approximately 1:0.6. Consequently, the total number of through holes 14d~14o (12 locations) in the region R3 below the straight line HL5 is greater than the total number of through holes 14a~14c (3 locations) in the region R3' above the straight line HL5. Therefore, the density of through holes 14d~14o in the region R3 below the straight line HL5 is higher than the density of through holes 14a~14c in the region R3' above the straight line HL5.

[0114] Furthermore, the total number of through-holes 14f to 14o (10 locations) within the area overlapping with the electric oil pump EOP (area R2 in the figure) was set to be greater than the total number of through-holes 14a to 14e (5 locations) within the area not overlapping with the EOP (area R2' in the figure).

[0115] As shown in Figure 7, in this embodiment, the height ratio between the region R2 below the line HL3 and the region R2' above the line HL3 is approximately 1:0.9. Consequently, the total number of through holes 14f~14o (10 locations) in the region R2 below the straight line HL3 is greater than the total number of through holes 14a~14e (5 locations) in the region R2' above the straight line HL3. Therefore, the density of through holes 14f~14o in the region R2 below the straight line HL3 is higher than the density of through holes 14a~14e in the region R2' above the straight line HL3.

[0116] Furthermore, more preferably, the total number of through holes 14h to 14o (8 locations) in the region below the straight line HL1 that passes through the point where the vibration of the electric oil pump EOP directly acts (region R1 in the figure) is greater than the total number of through holes 14a to 14g (7 locations) in the region above the straight line HL1 (region R1' in the figure).

[0117] As shown in Figure 7, in this embodiment, the height ratio between the region R1 below the straight line HL1 and the region R1' above the straight line HL1 is approximately 1:2. Consequently, the total number of through-holes 14h to 14o (8 locations) in region R1 below the straight line HL1 is greater than the total number of through-holes 14a to 14g (7 locations) in region R1' above the straight line HL1. Therefore, the density of through-holes 14h to 14o in region R1 below the straight line HL1 is higher than the density of through-holes 14a to 14g in region R1' above the straight line HL1.

[0118] By setting the distribution and density of the through-holes 14 involved in the mounting of the control valve CV in this way, the propagation of vibrations from the electric oil pump EOP to the control valve CV can be effectively suppressed.

[0119] Figure 8 illustrates a modified example. The electric oil pump (EOP) tends to experience vibrations in the pump section (933). Therefore, as shown in Figure 8, a bracket BK may be provided that is externally fitted to the pump section 933, and the bracket BK may be fixed to the bottom wall section 66 with bolts 16e and 16f. This configuration suppresses vibrations of the electric oil pump (EOP). This effectively prevents the transmission of vibrations from the electric oil pump (EOP) to the control valve (CV).

[0120] As described above, the case 6 (transmission case) of the vehicle power transmission device 1 according to this embodiment has the following configuration. (1) Case 6 (transmission case) has a bottom wall portion 66 that serves as a support wall for the control valve CV and the electric oil pump EOP (pump). The bottom wall section 66 (support wall) is It has a first region 661 to which a control valve CV is installed, and a second region 662 to which an electric oil pump EOP (pump) is installed. The first region 661 and the second region 662 are aligned in the horizontal direction along the rotation axis X of the power transmission device 1 (transmission). In the bottom wall portion 66, the total number of fastening points Pa to Po of the control valve CV in the region R2 that overlaps with the electric oil pump EOP when viewed from the horizontal direction (10 points) is greater than the total number of fastening points Pa to Pe in the region R2' that does not overlap with the electric oil pump EOP (5 points). The density of fastening points Pf~Po in region R2, which overlaps with the electric oil pump EOP, is higher than the density of fastening points Pa~Pe in region R2', which does not overlap with the electric oil pump EOP.

[0121] When the electric oil pump EOP is driven, vibrations are generated due to the operation of the pump unit 933. If the electric oil pump EOP and the control valve CV are supported by a common support wall, the vibrations generated in the electric oil pump EOP may be transmitted to the control valve CV via the bottom wall 66. If the control valve CV vibrates due to transmitted vibrations, the hydraulic pressure (operating hydraulic pressure) output from the control valve CV may fluctuate due to the vibration, potentially causing what is known as oil vibration. In such cases, the operation of the power transmission mechanism (e.g., variator 3) driven by the operating hydraulic pressure may be affected.

[0122] Vibrations from the electric oil pump EOP act on the bottom wall 66 from the fastening points Ta to Td of the electric oil pump EOP. In the bottom wall 66, the region closer to the fastening points Ta to Td of the electric oil pump EOP (the region involved in supporting the electric oil pump EOP) is more susceptible to vibration. Therefore, in the bottom wall portion 66, the number of fastening points of the control valve CV is increased in the region that overlaps with the electric oil pump EOP when viewed from the horizontal direction along the rotation axis X of the power transmission device 1 (transmission), that is, in the region close to the fastening points Ta to Td of the electric oil pump EOP, and the density of fastening points is also increased. This suppresses vibrations of the electric oil pump EOP that are transmitted to the control valve CV.

[0123] The control valve CV of the vehicle power transmission device 1 according to this embodiment has the following configuration. (2) The control valve CV is attached to the bottom wall portion 66 (support wall) of the case 6 (transmission case) of the power transmission device 1 together with the electric oil pump EOP (pump). In the bottom wall portion 66, the control valve CV and the electric oil pump EOP are aligned in a horizontal direction along the rotation axis X of the power transmission device 1 (transmission). The total number of fastening points Pa to Po with respect to the bottom wall portion 66 of the control valve CV is greater in the region R2 that overlaps with the electric oil pump EOP when viewed from the horizontal direction (10 points) than in the total number of fastening points Pa to Pe in the region R2' that does not overlap with the electric oil pump EOP (5 points). The density of fastening points Pf~Po in region R2, which overlaps with the electric oil pump EOP, is higher than the density of fastening points Pa~Pe in region R2', which does not overlap with the electric oil pump EOP.

[0124] This configuration makes it possible to suppress vibrations from the electric oil pump (EOP) that are transmitted to the control valve (CV).

[0125] The power transmission device 1 (transmission) for a vehicle according to this embodiment has the following configuration. (3) Power transmission device 1 is A control valve CV controls the hydraulic pressure supplied to the power transmission mechanism (gearbox), The electric oil pump EOP (pump) supplies oil OL to the control valve CV, The system comprises a case 6 (transmission case) having a bottom wall portion 66 that serves as a support wall for the control valve CV and the electric oil pump EOP. In the bottom wall portion 66, the control valve CV and the electric oil pump EOP are aligned in a horizontal direction along the rotation axis X of the power transmission device 1. In the bottom wall portion 66, the total number of fastening points Pa to Po of the control valve CV in the region R2 that overlaps with the electric oil pump EOP when viewed from the horizontal direction (10 points) is greater than the total number of fastening points Pa to Pe in the region R2' that does not overlap with the electric oil pump EOP (5 points). The density of fastening points Pf~Po in region R2, which overlaps with the electric oil pump EOP, is higher than the density of fastening points Pa~Pe in region R2', which does not overlap with the electric oil pump EOP.

[0126] This configuration makes it possible to suppress vibrations from the electric oil pump (EOP) that are transmitted to the control valve (CV).

[0127] (4) The control valve CV is mounted on the bottom wall 66 (support wall) with the operating valves (pressure regulating valve 97, control valve 98, switching valve 99, and solenoid 96) arranged in a vertical direction along the vertical line VL. The electric oil pump EOP is mounted on the bottom wall 66 with its rotating shaft Z1 aligned in the vertical direction. Solenoids 96a, 96b, and 96c are positioned so that they overlap with the electric oil pump EOP when viewed from the horizontal direction.

[0128] With this configuration, the solenoids 96a, 96b, and 96c of the control valve CV are located in region R2 (see Figure 6), which overlaps with the electric oil pump EOP when viewed from the horizontal direction. In the control valve CV, the thickness of the area where the solenoid 96 is located is greater than other areas by the thickness of the valve body (not shown) housed inside. Therefore, in the control valve CV, the rigidity of the region where the solenoids 96 are aligned vertically is higher than in other regions, making it less susceptible to the effects of vibrations transmitted from the electric oil pump EOP. By positioning the solenoid 96 in the region of the control valve CV where vibrations from the electric oil pump EOP propagate, the influence of vibrations from the electric oil pump EOP transmitted to the control valve CV can be suppressed.

[0129] (5) The solenoids 96 (96a~96d) are arranged with gaps between them in the vertical direction. The solenoids 96a, 96b, 96d, and 96c, and the fastening points P (Pc to Po) of the bolts 15 (15c to 15o) to the bottom wall 66 of the control valve CV are arranged alternately in the vertical direction.

[0130] With this configuration, when viewed from the front of the vehicle, the fastening points Pm, Pn, Po and solenoid 96a, the fastening points Pj, Pk, Pl and solenoid 96b, the fastening points Ph, Pi and solenoid 96c, and the fastening points Pf, Pg are arranged alternately in the vertical direction (see Figure 6). As a result, in the control valve CV, the fastening points by bolt 15 and the regions of the highly rigid solenoid 96 are arranged alternately in the vertical direction. Therefore, because the areas between the regions of the highly rigid solenoid 96 are fixed to the bottom wall 66, the control valve CV is less susceptible to the effects of vibrations transmitted from the electric oil pump EOP to the control valve CV.

[0131] (6) When viewed from the horizontal direction, the fastening points Ph and Pi of the bolts 15 to the bottom wall portion 66 of the control valve CV and the fastening points Ta and Tc of the bolts 16 to the bottom wall portion 66 of the electric oil pump EOP are set to be in an overlapping positional relationship. When viewed from the horizontal direction, the fastening points Pj, Pk, and Pl of the bolts 15 to the bottom wall 66 of the control valve CV and the fastening points Tb and Td of the bolts 16 to the bottom wall 66 of the electric oil pump EOP are set to overlap in position.

[0132] Vibrations from the electric oil pump EOP are input to the bottom wall 66 of the electric oil pump EOP from the fastening points Ta, Tb, Tc, and Td of the bolts 16 to the bottom wall 66. Therefore, by setting the fastening points Ph and Pi of the control valve CV to be in a positional relationship where they overlap when viewed from the horizontal, the fastening points Ta and Tc of the electric oil pump EOP, and the fastening points Pj, Pk and Pl of the control valve CV to be in a positional relationship where they overlap when viewed from the horizontal, it is possible to effectively prevent the control valve CV from vibrating excessively due to vibrations propagating from the fastening points Ta, Tb, Tc and Td along the horizontal.

[0133] In particular, by arranging the fastening points Pi and Pl of the control valve CV and the fastening points Ta and Tc of the electric oil pump EOP in close proximity, the vibration of the control valve CV can be suppressed near the point of application of vibration from the electric oil pump EOP. This improves the support stability of the control valve CV and reduces the influence of vibrations propagated from the electric oil pump EOP.

[0134] (7) When viewed from above along the vertical line VL with reference to the installation state of the power transmission device 1 on the vehicle V, the control valve CV has an overhang region Rw that extends to a position overlapping with the electric oil pump EOP. An overhang region Rw is provided where the fastening point Pg of the bolt 15 to the bottom wall portion 66 of the control valve CV is located.

[0135] Vibrations acting on the bottom wall portion 66 from the fastening points Ta to Td of the electric oil pump EOP propagate from the fastening points Ta to Td through the bottom wall portion 66. The overhang region Rw is located above the electric oil pump EOP. Therefore, by setting the fastening point Pg of the control valve CV in the overhang region Rw, the influence of vibrations propagating upward from the electric oil pump EOP on the control valve CV can be effectively suppressed.

[0136] In the above-described embodiment, the density of fastening points was explained using the height ratio of the control valve CV as an example. The height ratio is merely one example for explaining the difference in density. The density of fastening points may also be determined by the area ratio of the control valve CV when viewed from the front of the vehicle. Furthermore, in the above-described embodiment, the case was explained in which, among the fastening points Pa to Po of the control valve CV by the bolts 15 (15a to 15o), the total number of fastening points located on the lower side where the electric oil pump EOP is located is greater than the total number of fastening points located on the upper side, and the density of fastening points in the lower region is set to be higher than the density of fastening points in the upper region. However, the total number of fastening points located on the lower side where the electric oil pump EOP is located does not necessarily have to be greater than the total number of fastening points located on the upper side; it is sufficient that the density is set to be higher.

[0137] In the embodiment described above, the power transmission device 1 is shown as an example in which it transmits the rotation of the engine ENG to the drive wheels WH, WH. However, the power transmission device 1 may also transmit the rotation of at least one of the engine ENG and the motor (rotating electric machine) to the drive wheels WH, WH. For example, it may be a 1-motor, 2-clutch type power transmission device (a type in which a motor is placed between the engine ENG and the power transmission device, a first clutch is placed between the engine ENG and the motor, and a second clutch is placed inside the power transmission device 1). Furthermore, although the above-described embodiment illustrates a case where the power transmission device 1 has a speed change function, the power transmission mechanism may not have a speed change function and may simply reduce speed (or increase speed). If the power transmission device does not have a speed change function and is configured to reduce the rotation of the motor and transmit it to the drive wheels WH, WH, then the hydraulic control circuit for supplying the cooling oil OL for the motor and the lubricating oil OL for the reduction mechanism will be placed in the housing chamber S2 together with the electric oil pump EOP. Also, although the above-described embodiment illustrates a case where the control unit of the power transmission device 1 is equipped with a control valve CV, if the power transmission device 1 does not have a speed change mechanism and the drive source is a motor (rotating electricity) rather than an engine ENG, then the control unit may be equipped with an inverter or the like for driving and controlling the motor.

[0138] Although embodiments of the present invention have been described above, the present invention is not limited to the embodiments shown. It can be modified as appropriate within the scope of the technical idea of ​​the invention. [Explanation of Symbols]

[0139] 1. Power transmission device (power transmission mechanism) 2. Forward / reverse switching mechanism (power transmission mechanism) 3. Variator (power transmission mechanism) 4. Reduction mechanism (power transmission mechanism) 5. Differential (Power transmission mechanism) 6 cases (gearbox cases) 66 Bottom wall (support wall) 661 1st area 662 Second area 923 Notch 96 (96a~96d) Solenoid (operating valve) 97 (97a~97b) Pressure Regulating Valve (Operating Valve) 98 (98a, 98b) Control valve (operating valve) 99 Switching valve (operating valve) CV control valve EOP Electric Oil Pump (Pump) HS Housing (Transmission Case) Area overlapping with R2 electric oil pump R2' Area that does not overlap with the electric oil pump Rw Overhang Region T / C Torque Converter (Power Transmission Mechanism) Pa~Po control valve fastening point Ta~Td Fastening points of the electric oil pump (pump)

Claims

1. A transmission case having a support wall for a control valve and a pump, The aforementioned support wall is It has a first region to which the control valve is attached and a second region to which the pump is attached. The first region and the second region are aligned in the horizontal direction. A transmission case in which the density of fastening points of the control valve on the support wall is higher in the region overlapping the pump when viewed from the horizontal direction than in the region not overlapping the pump.

2. A control valve that is mounted together with the pump to the support wall of the transmission case, The control valve and the pump are arranged in the horizontal direction. A control valve wherein the density of fastening points of the control valve to the support wall is higher in the region overlapping the pump when viewed from the horizontal direction than in the region not overlapping the pump.

3. A control valve that controls the hydraulic pressure supplied to the transmission mechanism, A pump that supplies oil to the control valve, A transmission comprising the control valve and a transmission case having a support wall for the pump, In the support wall, the control valve and the pump are aligned in the horizontal direction. A transmission in which the density of fastening points of the control valve to the support wall is higher in the region overlapping the pump when viewed from the horizontal direction than in the region not overlapping the pump.

4. In claim 3, The control valve is mounted on the support wall in a manner that aligns the operating valves vertically. The pump is mounted on the support wall with its rotating shaft oriented along the vertical direction. The aforementioned operating valve is a transmission, which is positioned so as to overlap with the pump when viewed from the horizontal direction.

5. In claim 4, The aforementioned operating valves are arranged with spacing between them in the vertical direction. A transmission in which the fastening points of the operating valve and the control valve to the support wall are arranged alternately in the vertical direction.

6. In claim 5, A transmission in which, when viewed from the horizontal direction, the fastening point of the control valve to the support wall and the fastening point of the pump to the support wall are set to overlap in a relative position.

7. In any one of claims 4 to 6, Viewed from the above and below, the control valve has an overhang region that extends to a position overlapping the pump. A transmission in which at least one fastening point of the control valve to the support wall is provided in the overhang region.

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