JP2018173145A - Drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive device capable of reducing power consumption amount when fastening an engaging/disengaging means.SOLUTION: A drive device 100 includes: a drive device 102; a motor 102; a wheel W; a hydraulic clutch CL which is provided on a power transmission path; an electric oil pm EOP which supplies liquid pressure to the hydraulic clutch CL; and a hydraulic adjusting device OC1 which is connected with the electric oil pump EOP through an upstream side channel 103 and is connected with the hydraulic clutch CL through a downstream side channel 104. The hydraulic adjusting device OC1 brings the electric oil pump EOP and the hydraulic clutch CL into a communication state when the liquid pressure of the upstream side channel 103 is larger than a first predetermined value, thereby fastening the hydraulic clutch CL, and in a fastening state of the hydraulic clutch CL, brings the electric oil pump EOP and the hydraulic clutch CL into an intercepting state when the liquid pressure of the upstream side channel 103 becomes the first predetermined value or less, thereby keeping the fastening state of the hydraulic clutch.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a drive device in which a hydraulically driven connection / disconnection means is provided on a power transmission path between a drive source and a driven part.

  Patent Document 1 describes a drive device in which a hydraulically driven connection / disconnection means is provided on a power transmission path between a drive source and a driven part. According to Patent Document 1, after the connection / disconnection means is fastened during deceleration regeneration and reverse travel, power is continuously supplied to the two solenoid valves provided in the hydraulic circuit while the connection / disconnection means is maintained. It is described.

JP-A-2015-194244

  However, in the configuration described in Patent Document 1, it is necessary to continue to supply power to the two electromagnetic valves provided in the hydraulic circuit while maintaining the fastening of the connecting / disconnecting means during deceleration regeneration and reverse travel. There was room for improvement in terms of reducing power consumption.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a drive device that can reduce power consumption when fastening / disconnecting means.

In order to achieve the above object, the invention described in claim 1
A drive source (for example, an electric motor 102 of an embodiment described later);
A driven part that is driven by the driving source and propels the transportation mechanism (for example, a wheel W in an embodiment described later);
A hydraulically driven connecting / disconnecting means (for example, to be described later) is provided on a power transmission path between the drive source and the driven part and opens or closes the power transmission path. Form hydraulic clutch CL),
Hydraulic pressure supply means for supplying hydraulic pressure to the connecting / disconnecting means (for example, an electric oil pump EOP in an embodiment described later);
The hydraulic pressure supply means is connected to the upstream flow path (for example, the upstream flow path 103 in the embodiment described later), and the connecting / disconnecting means and the downstream flow path (for example, downstream of the embodiment described later). Hydraulic pressure adjusting devices (for example, hydraulic pressure adjusting devices OC1 and OC2 according to embodiments described later) connected via the side flow path 104),
The hydraulic pressure adjusting device is a non-electrically driven type, and switches the hydraulic pressure supply means and the connection / disconnection means to a communication state or a cutoff state in accordance with the hydraulic pressure of the upstream flow path (for example, a drive device (for example, A driving device 100) of an embodiment described later,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream flow path is greater than a first predetermined value, the hydraulic pressure supply means and the connection / disconnection means are brought into communication with each other to fasten the connection / disconnection means,
In the engaged state of the connection / disconnection means, the hydraulic pressure supply means and the connection / disconnection means are disconnected when the hydraulic pressure in the upstream-side flow path becomes equal to or lower than the first predetermined value. The fastening state of the contact means is maintained.

Moreover, in addition to the structure of Claim 1, the invention of Claim 2 is
The hydraulic pressure adjusting device adjusts the hydraulic pressure of the downstream flow path when the hydraulic pressure of the upstream flow path is equal to or lower than a second predetermined value smaller than the first predetermined value in the engaged state of the connection / disconnection means. The connection / disconnection means is released by opening.

Moreover, in addition to the structure of Claim 2, the invention of Claim 3 is
The fluid pressure adjusting device includes an upstream communication part (for example, an upstream communication part 105 in an embodiment described later) connected to the upstream flow path and a downstream communication part (connected to the downstream flow path ( For example, a downstream communication portion 106 of an embodiment described later), a valve body (for example, a valve body 111 of the embodiment described later), and a valve seat (for example, a valve seat 113 of the embodiment described later),
The valve body is provided so as to be seated on the valve seat from the downstream communication portion side so as to close the upstream communication portion,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream flow path is greater than the first predetermined value, the valve body is separated from the valve seat so that the hydraulic pressure supply means and the connection / disconnection means are in communication with each other,
The valve element is seated on the valve seat when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value in the engaged state of the connection / disconnection means. Thus, the hydraulic pressure supply means and the connection / disconnection means are brought into a disconnected state.

Moreover, in addition to the structure of Claim 3, the invention of Claim 4 adds to the structure of Claim 3,
The hydraulic pressure adjusting device includes a drain opening (for example, a drain opening 107 in an embodiment described later) for releasing the hydraulic pressure and a piston (for example, a communication section 110 in an embodiment described later) formed with a drain ( For example, a piston 109) of an embodiment described later is further provided,
The piston is provided with a pressure receiving surface (for example, a pressure receiving surface 114 in an embodiment described later) on the upstream side of the communication portion, and the valve seat is provided on the downstream side of the pressure receiving surface,
The hydraulic pressure adjusting device is
Due to the hydraulic pressure acting on the pressure receiving surface when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value, the piston opens from the downstream communication portion to the drain opening. Shut off
When the hydraulic pressure in the upstream flow path is equal to or less than the second predetermined value, the piston communicates the downstream communication part and the drain opening.

The invention according to claim 5
A driving source (for example, first and second electric motors 2A and 2B in the embodiments described later);
A driven part (for example, a rear wheel Wr in a later-described embodiment) driven by the drive source and propelling a transportation mechanism (for example, a vehicle 3 in a later-described embodiment);
A hydraulically driven connecting / disconnecting means (for example, to be described later) is provided on a power transmission path between the drive source and the driven part and opens or closes the power transmission path. Hydraulic brake 60) in the form of
A driving device (for example, a rear wheel driving device 1 according to an embodiment to be described later) including a hydraulic pressure supply unit (for example, an electric oil pump 70 according to an embodiment to be described later) for supplying hydraulic pressure to the connection / disconnection unit. And
The driving device includes a hydraulic circuit (for example, a line oil passage 75 in an embodiment described later) that communicates the hydraulic pressure supply unit and the connecting / disconnecting unit, and a first switch disposed on the hydraulic circuit. A valve (for example, a brake shift valve 74 in an embodiment described later) and a second switching valve (for example, an H / L solenoid valve 88 in an embodiment described later) capable of adjusting the hydraulic pressure of the hydraulic circuit. And
The first switching valve communicates with a valve body (for example, a valve body 74a in an embodiment described later) that can be switched between a first operation position and a second operation position, and the hydraulic pressure supply means, and the valve body A liquid chamber (for example, a valve body control chamber 74e in an embodiment described later) that houses a hydraulic medium that biases in the direction from the first operation position to the second operation position, and the valve body from the second operation position. Return means (for example, a spring 74d in an embodiment described later) for urging in the direction of the first operating position;
The second switching valve is electrically driven, and controls the hydraulic pressure of the hydraulic circuit to be greater than a first predetermined value when power is supplied, and sets the hydraulic pressure of the hydraulic circuit to a first value when power is not supplied. 1 Control to be below a predetermined value,
The driving device is further disposed on a liquid chamber circuit (for example, a second valve body control oil passage 79 in an embodiment described later) that communicates the liquid pressure supply means and the liquid chamber, and is electrically driven to operate by electric power. A third switching valve of a formula (for example, a brake solenoid valve 83 of an embodiment described later),
The third switching valve closes the liquid chamber circuit when power is supplied to shut off the liquid pressure supply means and the liquid chamber, and opens the liquid chamber circuit when power is not supplied. The pressure supply means and the liquid chamber are disposed so as to communicate with each other,
Between the third switching valve and the connecting / disconnecting means, a hydraulic pressure adjusting device (for example, hydraulic pressure adjusting devices OC1 and OC2 in embodiments described later) is provided,
The first switching valve is configured such that when the valve body is in the first operating position, the hydraulic circuit is opened so that the hydraulic pressure supply means and the hydraulic pressure adjusting device are in communication with each other, and the valve body Is disposed so that the hydraulic pressure circuit is closed when the second operating position, and the hydraulic pressure supply means and the hydraulic pressure adjusting device are cut off,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream-side flow path of the hydraulic pressure adjusting device is greater than the first predetermined value, the connecting / disconnecting means is fastened by bringing the hydraulic pressure supply means and the connecting / disconnecting means into communication. ,
In the engaged state of the connection / disconnection means, the hydraulic pressure supply means and the connection / disconnection means are disconnected when the hydraulic pressure in the upstream-side flow path becomes equal to or lower than the first predetermined value. The fastening state of the contact means is maintained.

Moreover, in addition to the structure of Claim 5, the invention of Claim 6 is
The hydraulic pressure adjusting device opens the hydraulic pressure in the downstream flow channel of the hydraulic pressure adjusting device when the hydraulic pressure in the upstream flow channel is equal to or lower than a second predetermined value that is smaller than the first predetermined value. , Release the connecting / disconnecting means.

Moreover, in addition to the structure of Claim 6, the invention of Claim 7 is
The fluid pressure adjusting device includes an upstream communication part (for example, an upstream communication part 105 in an embodiment described later) connected to the upstream flow path and a downstream communication part (connected to the downstream flow path ( For example, a downstream communication portion 106 of an embodiment described later), a valve body (for example, a valve body 111 of the embodiment described later), and a valve seat (for example, a valve seat 113 of the embodiment described later),
The valve body is provided so as to be seated on the valve seat from the downstream communication portion side so as to close the upstream communication portion,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream flow path is larger than the first predetermined value, the valve body is separated from the valve seat, so that the hydraulic pressure supply means and the connection / disconnection means are in communication with each other,
The valve element is seated on the valve seat when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value in the engaged state of the connection / disconnection means. Then, the hydraulic pressure supply means and the connection / disconnection means are brought into a disconnected state.

Moreover, in addition to the structure of Claim 7, invention of Claim 8 is added to the structure of Claim 7,
The hydraulic pressure adjusting device includes a drain opening (for example, a drain opening 107 in an embodiment described later) for releasing the hydraulic pressure and a piston (for example, a communication section 110 in an embodiment described later) formed with a drain ( For example, a piston 109) of an embodiment described later is further provided,
The piston is provided with a pressure receiving surface (for example, a pressure receiving surface 114 in an embodiment described later) on the upstream side of the communication portion, and the valve seat is provided on the downstream side of the pressure receiving surface,
The hydraulic pressure adjusting device is
Due to the hydraulic pressure acting on the pressure receiving surface when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value, the piston is removed from the downstream communication portion by the drain. Block the opening,
When the hydraulic pressure in the upstream flow path is equal to or less than the second predetermined value, the piston communicates the downstream communication part and the drain opening.

  According to the first aspect of the present invention, the hydraulic pressure adjusting device includes the hydraulic pressure supplying means and the connecting / disconnecting means when the hydraulic pressure in the upstream flow path becomes equal to or lower than the first predetermined value in the connected state of the connecting / disconnecting means. Can be maintained in the shut-off state, so that the hydraulic pressure in the downstream flow path can be maintained, whereby the fastening state of the connection / disconnection means can be maintained. Thereby, the electric power consumption of the hydraulic pressure supply means for maintaining the fastening state of the connection / disconnection means can be reduced.

  According to the second aspect of the present invention, the hydraulic pressure adjusting device releases the hydraulic pressure in the downstream flow path when the hydraulic pressure in the upstream flow path is equal to or lower than the second predetermined value in the engaged state of the connection / disconnection means. Therefore, the connection / disconnection means can be released.

  According to the invention described in claim 3, when the hydraulic pressure in the upstream flow path is larger than the first predetermined value, the valve body is separated from the valve seat, so that the hydraulic pressure supply means and the connection / disconnection means are communicated with each other. Can be in a state. Further, when the hydraulic pressure in the upstream flow path is larger than the second predetermined value and lower than the first predetermined value in the engaged state of the connecting / disconnecting means, the valve body is seated on the valve seat so that the hydraulic pressure is supplied. The means and the connecting / disconnecting means can be in a disconnected state.

  According to the fourth aspect of the present invention, when the hydraulic pressure in the upstream flow path is equal to or lower than the second predetermined value, the downstream communication section and the drain opening are communicated, so that the hydraulic pressure in the downstream flow path is Can be released.

According to the fifth aspect of the present invention, the hydraulic pressure adjusting device includes the hydraulic pressure supply means and the connecting / disconnecting means when the hydraulic pressure in the upstream flow path becomes equal to or lower than the first predetermined value in the connected state of the connecting / disconnecting means. By setting to the cut-off state, the fastening state of the connection / disconnection means can be maintained. Thereby, since it is not necessary to supply electric power to a 2nd switching valve in order to maintain the fastening of a connection / disconnection means, the power consumption of a 2nd switching valve can be reduced.
Further, since the first switching valve is in a natural state in which no hydraulic pressure is supplied to the liquid chamber, the valve body is in the first operating position and the hydraulic pressure supply means and the hydraulic pressure adjusting device are in communication with each other. The hydraulic pressure generated in the hydraulic pressure circuit immediately after startup can be immediately added to the hydraulic pressure adjusting device.
Further, in order to supply the hydraulic pressure to the connecting / disconnecting means, the liquid chamber circuit must be shut off, that is, the operation of the third switching valve is essential, so that the third switching valve cannot be operated (failure in which power cannot be supplied to other switching valves, When a failure that does not operate normally even if power is supplied to the other switching valve occurs, the connecting / disconnecting means is released and is not engaged unintentionally.

  According to the sixth aspect of the present invention, the hydraulic pressure adjusting device can release the connecting / disconnecting means by releasing the hydraulic pressure of the downstream flow path when it is equal to or lower than the second predetermined value of the upstream flow path. it can.

  According to the seventh aspect of the present invention, when the hydraulic pressure in the upstream channel is larger than the second predetermined value, the valve body is separated from the valve seat, so that the hydraulic pressure supply means and the hydraulic pressure adjusting device are It can be in a communication state. Further, when the hydraulic pressure in the upstream flow path is larger than the second predetermined value and lower than the first predetermined value in the engaged state of the connecting / disconnecting means, the valve body is seated on the valve seat so that the hydraulic pressure is supplied. The means and the hydraulic pressure adjusting device can be cut off.

  According to the eighth aspect of the invention, when the fluid pressure in the upstream channel is equal to or lower than the second predetermined value, the fluid pressure in the downstream channel is communicated with the downstream communication portion and the drain opening. Can be released.

It is a schematic block diagram of the drive device which concerns on 1st Embodiment of this invention. It is explanatory drawing which shows the mode of the hydraulic adjustment apparatus when an electric oil pump is a high voltage | pressure drive state. It is explanatory drawing which shows the mode of the hydraulic control apparatus when an electric oil pump is made into a low voltage | pressure drive state in the fastening state of a hydraulic clutch. It is explanatory drawing which shows the mode of the hydraulic control apparatus when an electric oil pump is made into a non-driving state in the fastening state of a hydraulic clutch. It is a schematic block diagram of the hydraulic control apparatus which concerns on a modification. It is a schematic block diagram of the vehicle carrying the drive device which concerns on 2nd Embodiment of this invention. It is a longitudinal cross-sectional view of one Embodiment of a rear-wheel drive device. FIG. 6 is a partially enlarged view of the rear wheel drive device shown in FIG. 5. 1 is a hydraulic circuit diagram showing an embodiment of a hydraulic circuit. (A) is explanatory drawing of the regulator valve in the state where the valve body stopped at the 1st position, (b) is explanatory drawing of the regulator valve in the state where the valve body stopped at the 2nd position. (A) is explanatory drawing of the brake shift valve of the state which the valve body stood in the 2nd operation position, (b) is explanatory drawing of the brake shift valve of the state which the valve body stopped in the 1st operation position. It is a hydraulic circuit diagram which shows the hydraulic circuit in the fastening state of a hydraulic brake. It is a hydraulic circuit diagram which shows the hydraulic circuit in the weak engagement state of a hydraulic brake. FIG. 3 is a hydraulic circuit diagram showing a hydraulic circuit in a released state of a hydraulic brake during traveling. FIG. 2 is a hydraulic circuit diagram showing a hydraulic circuit in a released state of a hydraulic brake while the vehicle is stopped. It is a speed alignment chart of the rear-wheel drive device in a stop. It is a speed alignment chart of the rear-wheel drive device at the time of forward low vehicle speed. It is a speed alignment chart of the rear-wheel drive device at the time of forward vehicle speed. It is a speed alignment chart of the rear-wheel drive device at the time of deceleration regeneration. It is a speed alignment chart of the rear-wheel drive device at the time of forward high vehicle speed. It is a speed alignment chart of the rear-wheel drive device at the time of reverse drive. It is a timing chart in an example of vehicle running.

  Hereinafter, embodiments of a drive device according to the present invention will be described with reference to the drawings.

<First Embodiment>
As shown in FIG. 1, the drive device 100 of the first embodiment is driven by an electric motor 102 as a drive source, a wheel W as a driven portion of a vehicle as a transport mechanism, an electric motor 102 and a wheel. A hydraulic clutch CL as a hydraulic drive type connecting / disconnecting means which is provided on a power transmission path with W and is released or fastened to make the power transmission path in a disconnected state or a connected state, and a hydraulic pressure is applied to the hydraulic clutch CL. And an electric oil pump EOP serving as a hydraulic pressure supply means.

  Further, on the hydraulic pressure transmission path between the electric oil pump EOP and the hydraulic clutch CL, the electric oil pump EOP and the upstream flow path 103 are connected, and the hydraulic clutch CL and the downstream flow path 104 are connected. An oil pressure adjusting device OC1 is provided.

  The hydraulic pressure adjustment device OC1 is non-electrically driven, and switches the electric oil pump EOP and the hydraulic clutch CL to the communication state or the cutoff state according to the hydraulic pressure of the upstream flow path 103. More specifically, the hydraulic pressure adjusting device OC1 includes an upstream communication unit 105 connected to the upstream channel 103, a downstream communication unit 106 connected to the downstream channel 104, and a drain chamber (not shown). The drain opening 107 connected to the upstream side, the upstream side communication part 105, the downstream side communication part 106, and the drain adjustment part 108 are slidably provided, and the upstream side communication part 105 and the downstream side are provided. The piston 109 in which the communication part 110 which connects the side communication part 106 is formed, the valve body 111 provided in the communication part 110 of the piston 109, the spring 112 which urges the valve body 111, and the valve body 111 are seated. And a valve seat 113.

  The piston 109 has a piston base portion 109a having a pressure receiving surface 114 for receiving the hydraulic pressure supplied from the upstream side communication portion 105 provided on the bottom surface, and a hollow shape in which a communication portion 110 is formed inside the piston base portion 109a. A piston columnar portion 109b. The pressure receiving surface 114 is formed with a pressure receiving surface opening 109 c that is connected to the communication portion 110. The pressure receiving surface opening 109c has a smaller diameter than the communication portion 110, and is formed in a funnel shape by gradually reducing the diameter between the pressure receiving surface opening 109c and the communication portion 110 from the communication portion 110 toward the pressure receiving surface opening 109c. This funnel-shaped portion is a valve seat 113 on which the valve body 111 is seated. The valve body 111 is a spherical body, and is biased toward the valve seat 113 by a spring 112 whose one end abuts on the top surface 108 a of the hydraulic pressure adjustment chamber 108 and whose other end abuts on the valve body 111.

  Next, the operation of the hydraulic pressure adjusting device OC1 will be described with reference to FIGS. 2A to 2C. The electric oil pump EOP can be in a non-driving state, a low-pressure driving state, and a high-pressure driving state. When the electric oil pump EOP is in the non-driving state, the hydraulic pressure in the upstream flow path 103 is equal to or less than a second predetermined value (for example, substantially zero), and when the electric oil pump EOP is in the low pressure driving state, the hydraulic pressure in the upstream flow path 103 is When the electric oil pump EOP is in the high pressure driving state, the hydraulic pressure in the upstream flow path 103 is greater than the first predetermined value.

  In the initial state shown in FIG. 1, that is, when the electric oil pump EOP is not driven, no hydraulic pressure is supplied to the pressure receiving surface 114 of the piston 109, and the pressure receiving surface 114 is seated on the bottom surface 108 b of the hydraulic pressure adjustment chamber 108. In addition, the valve body 111 is also seated on the valve seat 113, so that the downstream side communication portion 106 and the drain opening portion 107 communicate with each other, and the downstream side communication portion 106, the drain opening portion 107, and the upstream side communication portion 105 communicated with each other. Is shut off. Accordingly, no hydraulic pressure is supplied to the downstream flow path 104, and the hydraulic clutch CL is in a released state.

  When the electric oil pump EOP is brought into a high pressure driving state from this state, as shown in FIG. 2A, the hydraulic pressure of the upstream flow path 103 becomes larger than the first predetermined value, and the piston acts by the hydraulic pressure acting on the pressure receiving surface 114 of the piston 109. 109 is separated from the bottom surface 108b of the hydraulic pressure adjusting chamber 108. Subsequently, the hydraulic pressure acting on the valve body 111 from the pressure receiving surface opening 109c is larger than the urging force acting on the valve body 111 by the spring 112. Separated from the seat 113. Thereby, since the piston columnar portion 109b of the piston 109 seals the drain opening 107, the upstream communication portion 105 and the downstream communication portion 106 communicate with each other, and the upstream communication portion 105 and the downstream communication portion communicated with each other. 106 and the drain opening 107 are blocked. Then, the oil that has passed through the gap between the valve body 111 and the valve seat 113 from the pressure receiving surface opening 109c is supplied from the downstream communication portion 106 to the hydraulic clutch CL via the downstream flow path 104, and the hydraulic clutch CL is fastened.

  Subsequently, when the electric oil pump EOP is in the low pressure driving state in the engaged state of the hydraulic clutch CL, as shown in FIG. 2B, the hydraulic pressure of the upstream flow path 103 is larger than the second predetermined value and the first predetermined value. Although the piston 109 is separated from the bottom surface 108b of the hydraulic pressure adjusting chamber 108 by the hydraulic pressure acting on the pressure receiving surface 114 of the piston 109, the spring 112 is more effective than the hydraulic pressure acting on the valve body 111 from the pressure receiving surface opening 109c. Therefore, the urging force acting on the valve body 111 is large, so that the valve body 111 is seated on the valve seat 113. As a result, the piston columnar portion 109b of the piston 109 seals the drain opening 107 and the valve body 111 seals the pressure receiving surface opening 109c, so that the downstream communication portion 106 and the drain opening 107 are blocked. The downstream communication unit 106 and the upstream communication unit 105 are blocked. That is, in this state, although the electric oil pump EOP is in the low pressure driving state, the hydraulic pressure of the downstream side communication unit 106 is maintained and the engaged state of the hydraulic clutch CL can be maintained.

  To make the hydraulic clutch CL disengaged from this state, the electric oil pump EOP may be brought into a non-driving state. When the electric oil pump EOP is in a non-driven state, as shown in FIG. 2C, the hydraulic pressure in the upstream flow path 103 is equal to or lower than a second predetermined value, so that the pressure receiving surface 114 remains with the valve body 111 sitting on the valve seat 113 It sits on the bottom surface 108b of the hydraulic adjustment chamber 108. As a result, the downstream communication portion 106 and the drain opening portion 107 communicate with each other, and the communicated downstream communication portion 106 and drain opening portion 107 and the upstream communication portion 105 are blocked. Accordingly, the hydraulic pressure of the downstream side flow path 104 is released, and the hydraulic clutch CL is released.

  As described above, according to the present embodiment, the hydraulic pressure adjusting device OC1 changes the electric oil pump EOP from the high pressure driving state to the low pressure driving state in the engaged state of the hydraulic clutch CL, and the hydraulic pressure of the upstream flow path 103 is the first. When the electric oil pump EOP and the hydraulic clutch CL are disconnected when the predetermined value or less is reached, the hydraulic pressure of the downstream flow path 104 can be maintained, and the engaged state of the hydraulic clutch CL can be maintained. That is, since the engagement state of the hydraulic clutch CL is maintained even when the electric oil pump EOP is in the low pressure driving state, the electric oil pump EOP only needs to be in the high pressure driving state when the hydraulic clutch CL is engaged, and the hydraulic clutch CL is maintained. Therefore, the power consumption of the electric oil pump EOP can be reduced.

  The hydraulic pressure adjustment device OC1 includes an upstream communication portion 105 connected to the upstream flow passage 103, a downstream communication portion 106 connected to the downstream flow passage 104, a valve body 111, a valve seat 113, And the valve body 111 is provided so as to be seated on the valve seat 113 from the downstream communication portion 106 side so as to close the upstream communication portion 105, so that when the hydraulic pressure of the upstream flow path 103 is larger than the first predetermined value When the valve body 111 is separated from the valve seat 113, the electric oil pump EOP and the hydraulic clutch CL can be brought into communication. Further, in the engaged state of the hydraulic clutch CL, the valve body 111 is seated on the valve seat 113 when the hydraulic pressure in the upstream flow path 103 is larger than the second predetermined value and lower than the first predetermined value, thereby The oil pump EOP and the hydraulic clutch CL can be disconnected.

  Further, the hydraulic pressure adjusting device OC1 releases the hydraulic pressure of the downstream flow path 104 when the hydraulic pressure of the upstream flow path 103 is equal to or lower than the second predetermined value in the engaged state of the hydraulic clutch CL, so that the electric oil pump EOP is not driven. By setting the state, the hydraulic clutch CL can be released.

  That is, the hydraulic pressure adjustment device OC1 further includes a drain opening 107 that releases hydraulic pressure, and a piston 109 in which the communication portion 110 is formed, and the hydraulic pressure of the upstream flow path 103 is greater than a second predetermined value and 1 The piston 109 blocks the drain opening 107 from the upstream communication portion 105 and the downstream communication portion 106 by the hydraulic pressure acting on the pressure receiving surface 114 when the pressure is less than a predetermined value, and the hydraulic pressure of the upstream flow passage 103 is a second predetermined pressure. When the value is less than or equal to the value, the downstream side communication portion 106 and the drain opening portion 107 are communicated. Therefore, when the upstream side flow passage 103 has a hydraulic pressure equal to or lower than the second predetermined value, the downstream side flow passage 104 can be released by connecting the downstream communication portion 106 and the drain opening 107.

<Modification>
Next, a modification of the drive device 100 of the first embodiment will be described with reference to FIG. Note that the drive device of this modification is different from the hydraulic pressure adjustment device OC1 of the first embodiment in the configuration of the hydraulic pressure adjustment device, so only the differences will be described in detail, and the same or equivalent configurations will be denoted by the same reference numerals. Therefore, the description is omitted.

  In the hydraulic pressure adjusting device OC2 of this modification, in addition to the valve body 111, the spring 112, and the valve seat 113, a cylindrical shape arranged to surround the periphery of the valve body 111 at the communicating portion 110 of the piston 109. And a spring 121 having one end in contact with the top surface 108a of the hydraulic pressure adjusting chamber 108 and the other end in contact with the collar 120. That is, in this modification, the piston 109 is pressed to the bottom surface 108 b side of the hydraulic pressure adjustment chamber 108 by the spring 121 through the collar 120. Oil can pass between the collar 120 and the valve body 111.

  According to such a hydraulic pressure adjusting device OC2, when the electric oil pump EOP is brought into the high pressure driving state from the released state of the hydraulic clutch CL, the hydraulic pressure of the upstream flow path 103 becomes larger than the first predetermined value. Since the hydraulic pressure acting on the valve body 111 from the opening 109 c is larger than the urging force acting on the valve body 111 by the spring 112, the valve body 111 is separated from the valve seat 113. At this time, the urging force acting on the piston 109 via the collar 120 by the spring 121 is larger than the hydraulic pressure acting on the pressure receiving surface 114 of the piston 109, so the piston 109 is seated on the bottom surface 108 b of the hydraulic pressure adjustment chamber 108.

  Subsequently, when the hydraulic pressure acting on the pressure receiving surface 114 of the piston 109 becomes larger than the urging force acting on the piston 109 via the collar 120 by the spring 121, the piston 109 is separated from the bottom surface 108 b of the hydraulic pressure adjustment chamber 108. Thereby, the upstream communication portion 105 and the downstream communication portion 106 communicate with each other, and the communicated upstream communication portion 105 and downstream communication portion 106 and the drain opening 107 are blocked. Then, oil that has passed through the gap between the valve element 111 and the valve seat 113 from the pressure receiving surface opening 109c is supplied from the downstream communication portion 106 to the hydraulic clutch CL via the downstream flow path 104, and the hydraulic clutch CL is fastened. That is, in the hydraulic pressure adjusting device OC2 of the present modification, the valve body 111 is separated from the valve seat 113 before the piston 109 is separated from the bottom surface 108b of the hydraulic pressure adjusting chamber 108, so that the electric oil pump EOP is driven from the non-driven state to the high pressure. As a state, the response when the hydraulic clutch CL is changed from the released state to the engaged state is improved.

  Note that, in the engaged state of the hydraulic clutch CL, the operation of the hydraulic adjustment device OC2 when the electric oil pump EOP is in the low pressure driving state, and the operation of the hydraulic adjustment device OC2 when the hydraulic clutch CL is released from this state Since is the same as the hydraulic pressure adjustment device OC1 of the first embodiment, the description thereof is omitted.

Second Embodiment
The drive device 1 of 2nd Embodiment is used for the vehicle of a drive system as shown, for example in FIG. In the following description, a case where the driving device is used for driving the rear wheels will be described as an example, but it may be used for driving the front wheels.

[vehicle]
First, a vehicle on which the drive device of the present invention can be mounted will be described taking a hybrid vehicle as an example.
A vehicle 3 shown in FIG. 4 is a hybrid vehicle having a driving device 6 (hereinafter referred to as a front wheel driving device) in which an internal combustion engine 4 and an electric motor 5 are connected in series at the front portion of the vehicle. Is transmitted to the front wheels Wf via the transmission 7, while the power of the driving device 1 (hereinafter referred to as a rear wheel driving device) provided at the rear of the vehicle separately from the front wheel driving device 6 is the rear wheel Wr. (RWr, LWr). The electric motor 5 of the front wheel drive device 6 and the first and second electric motors 2A and 2B of the rear wheel drive device 1 are connected to the battery 9 so that power supply from the battery 9 and energy regeneration to the battery 9 are possible. ing. Reference numeral 8 denotes a control device for performing various controls of the entire vehicle.

[Rear wheel drive device]
FIG. 5 is a longitudinal sectional view of the entire rear wheel drive device 1. In FIG. 5, 10A and 10B are left and right axles on the rear wheel Wr side of the vehicle 3, which are coaxial in the vehicle width direction. Is arranged. A case 11 of the rear wheel drive device 1 is formed in a substantially cylindrical shape as a whole, and includes therein first and second motors 2A and 2B for driving an axle and driving of the first and second motors 2A and 2B. The first and second planetary gear type speed reducers 12A and 12B that reduce the rotation are arranged coaxially with the axles 10A and 10B. The first motor 2A and the first planetary gear type speed reducer 12A function as a left wheel driving device that drives the left rear wheel LWr, and the second motor 2B and the second planetary gear type speed reducer 12B drive the right rear wheel RWr. The first electric motor 2A and the first planetary gear type speed reducer 12A, the second electric motor 2B and the second planetary gear type speed reducer 12B are symmetrical in the vehicle width direction in the case 11. Has been placed.

  The rear wheel drive device 1 is provided with a breather device 40 that communicates the inside and outside of the case 11 so that the air inside the case 11 escapes to the outside through the breather chamber 41 so that the air does not become excessively high temperature and pressure. Configured as follows. The breather chamber 41 is disposed at the upper part in the vertical direction of the case 11, and includes an outer wall of the central case 11M, a first cylindrical wall 43 extending substantially horizontally in the central case 11M on the left side case 11A side, and a right side case. A second cylindrical wall 44 extending substantially horizontally on the 11B side, a left and right dividing wall 45 connecting the inner ends of the first and second cylindrical walls 43, 44, and a left side case 11A of the first cylindrical wall 43. A space formed by a baffle plate 47A attached so as to abut on the side tip, and a baffle plate 47B attached so as to abut on the right side case 11B side tip of the second cylindrical wall 44. The

  The first and second cylindrical walls 43 and 44 and the left and right dividing walls 45 that form the lower surface of the breather chamber 41 are such that the first cylindrical wall 43 is positioned radially inward from the second cylindrical wall 44, and the left and right dividing walls 45 are A third cylinder that extends from the inner end of the second cylindrical wall 44 to the inner end of the first cylindrical wall 43 while being bent while reducing the diameter, and further extends radially inward and extends substantially horizontally. Reach wall 46. The third cylindrical wall 46 is located on the inner side of both outer end portions of the first cylindrical wall 43 and the second cylindrical wall 44 and substantially in the center thereof.

  In the central case 11M, baffle plates 47A and 47B are provided in the space between the first cylindrical wall 43 and the outer wall of the central case 11M or the space between the second cylindrical wall 44 and the outer wall of the central case 11M as the first planet. It is fixed so as to be separated from the gear type speed reducer 12A or the second planetary gear type speed reducer 12B.

  In addition, an external communication path 49 that connects the breather chamber 41 and the outside is connected to the central case 11M on the upper surface in the vertical direction of the breather chamber 41. The breather chamber side end portion 49a of the external communication passage 49 is arranged so as to be directed downward in the vertical direction. Accordingly, the oil is prevented from being discharged to the outside through the external communication passage 49.

  In the first and second electric motors 2A and 2B, stators 14A and 14B are fixed to side cases 11A and 11B, respectively, and annular rotors 15A and 15B are rotatably arranged on the inner peripheral sides of the stators 14A and 14B. Yes. Cylindrical shafts 16A and 16B surrounding the outer periphery of the axles 10A and 10B are coupled to the inner peripheral portions of the rotors 15A and 15B, and the cylindrical shafts 16A and 16B can be relatively rotated coaxially with the axles 10A and 10B. The side cases 11A and 11B are supported by end walls 17A and 17B and partition walls 18A and 18B via bearings 19A and 19B. Further, on the outer periphery of one end side of the cylindrical shafts 16A and 16B and on the end walls 17A and 17B, the rotational position information of the rotors 15A and 15B is sent to the controller of the first and second electric motors 2A and 2B (not shown). Resolvers 20A and 20B are provided for feedback. The first and second electric motors 2A and 2B including the stators 14A and 14B and the rotors 15A and 15B have the same radius, and the first and second electric motors 2A and 2B are arranged in mirror symmetry with each other. The axle 10A and the cylindrical shaft 16A pass through the first electric motor 2A and extend from both ends of the first electric motor 2A. The axle 10B and the cylindrical shaft 16B also penetrate the second electric motor 2B. , Extending from both ends of the second electric motor 2B.

  The first and second planetary gear speed reducers 12A and 12B include sun gears 21A and 21B, ring gears 24A and 24B positioned on the outer peripheral side of the sun gears 21A and 21B, and the sun gears 21A and 21B and the ring gears 24A and 24B. A plurality of planetary gears 22A, 22B meshing with each other, and planetary carriers 23A, 23B that support these planetary gears 22A, 22B. The decelerated driving force is output to the axles 10A and 10B through the planetary carriers 23A and 23B.

  The sun gears 21A and 21B are formed integrally with the cylindrical shafts 16A and 16B. The planetary gears 22A and 22B are double pinions having first pinions 26A and 26B having large diameters directly meshed with the sun gears 21A and 21B, and second pinions 27A and 27B having smaller diameters than the first pinions 26A and 26B. The first pinions 26A and 26B and the second pinions 27A and 27B are integrally formed in a state of being coaxial and offset in the axial direction. The planetary gears 22A and 22B are supported by the pinion shafts 32A and 32B of the planetary carriers 23A and 23B via needle bearings 31A and 31B. 10B and is supported by the partition walls 18A and 18B via bearings 33A and 33B.

  The ring gears 24A and 24B have gear portions 28A and 28B that are meshed with the second pinions 27A and 27B whose inner peripheral surfaces are small diameters, and small diameters that are smaller than the gear portions 28A and 28B and that are opposed to each other at an intermediate position of the case 11. Parts 29A, 29B, and connecting parts 30A, 30B for connecting the axially inner ends of the gear parts 28A, 28B and the axially outer ends of the small diameter parts 29A, 29B in the radial direction.

  The gear portions 28A and 28B face each other in the axial direction with a third cylindrical wall 46 formed at the inner diameter side end portion of the left and right dividing wall 45 of the central case 11M. The outer diameter surfaces of the small diameter portions 29A and 29B are spline-fitted to an inner race 51 of a one-way clutch 50, which will be described later, and the ring gears 24A and 24B are connected to each other so as to rotate integrally with the inner race 51 of the one-way clutch 50. Configured.

  On the second planetary gear type speed reducer 12B side, between the second cylindrical wall 44 of the central case 11M constituting the case 11 and the gear portion 28B of the ring gear 24B, a hydraulic brake constituting braking means for the ring gear 24B 60 is arranged so as to overlap with the first pinion 26B in the radial direction and overlap with the second pinion 27B in the axial direction. The hydraulic brake 60 includes a plurality of fixed plates 35 that are spline-fitted to the inner peripheral surface of the second cylindrical wall 44 and a plurality of rotary plates 36 that are spline-fitted to the outer peripheral surface of the gear portion 28B of the ring gear 24B. These plates 35 and 36 are arranged so as to be fastened and released by an annular piston 37. The piston 37 is accommodated in an annular cylinder chamber formed between the left and right dividing walls 45 of the central case 11M and the third cylindrical wall 46, and is further provided with a receiving provided on the outer peripheral surface of the third cylindrical wall 46. The elastic member 39 supported by the seat 38 is constantly urged in a direction to release the fixed plate 35 and the rotating plate 36.

  More specifically, the working chamber S into which oil is directly introduced is defined between the left and right dividing walls 45 and the piston 37, and when the pressure of the oil introduced into the working chamber S exceeds the urging force of the elastic member 39, The piston 37 moves forward (to the right), and the fixed plate 35 and the rotating plate 36 are pressed against each other and fastened. When the urging force of the elastic member 39 exceeds the pressure of the oil introduced into the working chamber S, the piston 37 moves backward (leftward movement), and the fixed plate 35 and the rotating plate 36 are separated and released. . The working chamber S is connected via a hydraulic circuit 71 to an electrically driven electric oil pump 70 (see FIG. 4) driven by an oil pump electric motor 90 as hydraulic pressure supply means.

  In the case of this hydraulic brake 60, the fixed plate 35 is supported by the second cylindrical wall 44 extending from the left and right dividing walls 45 of the central case 11M constituting the case 11, while the rotating plate 36 is supported by the gear portion 28B of the ring gear 24B. Therefore, when the plates 35 and 36 are pressed by the piston 37, a braking force is applied to the ring gear 24B by the frictional engagement between the plates 35 and 36, and is fixed. When the fastening by the piston 37 is released from this state, the ring gear 24B is allowed to rotate freely. As described above, since the ring gears 24A and 24B are connected to each other, the braking force is also applied to the ring gear 24A by fastening the hydraulic brake 60, and the ring gear 24A is also fixed by releasing the hydraulic brake 60. Free rotation is allowed.

  Also, a space is secured between the coupling portions 30A and 30B of the ring gears 24A and 24B facing each other in the axial direction, and only power in one direction is transmitted to the ring gears 24A and 24B in the space to transmit power in the other direction. A one-way clutch 50 is arranged to be shut off. The one-way clutch 50 has a large number of sprags 53 interposed between an inner race 51 and an outer race 52. The inner race 51 is connected to the small diameter portions 29A, 29B of the ring gears 24A, 24B by spline fitting. It is configured to rotate integrally. The outer race 52 is positioned by the third cylindrical wall 46 and is prevented from rotating.

  The one-way clutch 50 is configured to engage and lock the rotation of the ring gears 24A and 24B when the vehicle 3 moves forward with the power of the first and second electric motors 2A and 2B. More specifically, in the one-way clutch 50, when the rotational power in the forward direction (the rotational direction when the vehicle 3 is advanced) on the first and second electric motors 2A, 2B side is input to the rear wheel Wr side. Is engaged, and the first and second electric motors 2A, 2B are in the non-engaged state when the reverse rotational power is input to the rear wheel Wr, and the forward rotational power is applied to the rear wheel Wr. Is disengaged when the first and second electric motors 2A and 2B are input, and the reverse rotational power on the rear wheel Wr side is input to the first and second electric motors 2A and 2B. Is engaged.

  As described above, in the rear wheel drive device 1 of the present embodiment, the one-way clutch 50 and the hydraulic brake 60 are provided in parallel on the power transmission path between the first and second electric motors 2A and 2B and the rear wheel Wr. . Note that an oil storage portion T for storing oil is formed below the case 11, and the oil surface height is such that the lower ends of the rotors 15A and 15B of the first and second electric motors 2A and 2B are not submerged. In FIG. 5, the symbol H).

[Hydraulic circuit]
Here, the hydraulic circuit 71 constituting the rear wheel drive device 1 will be described with reference to FIGS.
As shown in FIG. 7, the hydraulic circuit 71 decompresses the oil sucked from the oil suction port 70 a disposed in the oil reservoir T and discharged from the electric oil pump 70, and the first and second motors 2 </ b> A, 2 </ b> B, A regulator valve 73 that supplies the lubrication / cooling unit 91 such as the first and second planetary gear speed reducers 12A and 12B, and a brake shift that selectively permits and blocks the supply of oil to the working chamber S of the hydraulic brake 60. The valve 74, the H / L solenoid valve 88 that switches the valve position of the regulator valve 73, the brake solenoid valve 83 that switches the valve position of the brake shift valve 74, and the hydraulic pressure adjusting device OC1 described above are provided. The electric oil pump 70, the regulator valve 73, the brake shift valve 74, the H / L solenoid valve 88, the brake solenoid valve 83, and the hydraulic pressure adjustment device OC <b> 1 are connected via a line oil passage 75. Note that the configuration of the hydraulic pressure adjustment device OC1 is the same as that of the first embodiment, and thus detailed description thereof is omitted. Further, instead of the hydraulic pressure adjusting device OC1 of the first embodiment, a hydraulic pressure adjusting device OC2 of a modified example may be used.

  The regulator valve 73 includes a valve body 73a that is slidably accommodated in the valve accommodating chamber, an annular supply port 73b that is formed on the inner peripheral surface of the substantially central portion of the valve accommodating chamber and communicates with the line oil passage 75, An annular discharge port 73c formed at a position adjacent to the supply port 73b and communicating with the lubrication / cooling section 91 via the lubrication / cooling oil passage 76, and formed on the opposite side of the supply port 73b across the discharge port 73c An annular line pressure introduction port 73d that communicates with the line oil passage 75 and a spring that is disposed on one end side (left side in the figure) of the valve storage chamber and biases the valve body 73a to the other end side (right side in the figure). 73e, and a valve body control port 73f that is provided on the other end side of the valve storage chamber and into which the line pressure of the line oil passage 75 is selectively introduced by the H / L solenoid valve 88.

  The H / L solenoid valve 88 is a two-position, three-port switching valve having a valve body (ball) that is operated by turning the solenoid on (power supply) or off (no power supply). A connected line side port 88a, a valve side port 88b connected to the first valve body control oil passage 78 connected to the valve body control port 73f of the regulator valve 73, and a drain port 88c connected to the drain passage. ing. The H / L solenoid valve 88 is ON / OFF controlled by the control device 8, and at the time of ON control, the line side port 88a and the valve side port 88b are shut off, and the valve side port 88b and the drain port 88c are connected to each other. The supply of the line pressure of the line oil passage 75 to the body control port 73f is shut off, and the line side port 88a and the valve side port 88b are connected and the valve side port 88b and the drain port 88c are shut off during off control. The line pressure of the line oil passage 75 is applied to the distal end surface 73a1 of the valve body 73a through the body control port 73f.

In the regulator valve 73, as shown in FIG. 8A, when the H / L solenoid valve 88 is controlled to be turned off (OFF), the line oil passage 75 is connected to the distal end surface 73a1 of the valve body 73a through the valve body control port 73f. The line pressure of the line oil passage 75 acts on the annular groove 73a2 of the valve body 73a through the line pressure introduction port 73d. The valve body 73a has a wall surface of the valve housing chamber and a constricted portion 73a3 of the valve body 73a due to a balance between the hydraulic load applied to the valve body 73a through the valve body control port 73f and the line pressure introduction port 73d and the spring load of the spring 73e. clearance _{T OFF} is stationary at the position (first position) to be formed, a supply port 73b and exhaust port 73c is connected through a gap _{T OFF} during.

On the other hand, as shown in FIG. 8B, when the H / L solenoid valve 88 is turned on (ON), the supply of the line pressure of the line oil passage 75 to the valve body control port 73f is cut off, and the line The line pressure of the line oil passage 75 acts on the annular groove 73a2 of the valve body 73a through the pressure introduction port 73d. The valve body 73a has a gap T _ON between the wall surface of the valve housing chamber and the constricted portion 73a3 of the valve body 73a due to the balance between the hydraulic load applied to the valve body 73a through the line pressure introduction port 73d and the spring load of the spring 73e. There stationary position (second position) which is formed, a supply port 73b and exhaust port 73c is connected through a gap T _ON.

Thus, depending on whether the H / L solenoid valve 88 is off-controlled (OFF) or on-controlled (ON), hydraulic pressure is applied in a direction against the spring load of the spring 73e (leftward in FIG. 8). The pressure receiving area of the valve body 73a is changed, and the pressure receiving area when the H / L solenoid valve 88 is OFF-controlled (OFF) is larger than the pressure receiving area when the H / L solenoid valve 88 is ON-controlled (ON). On the other hand, regardless of whether the H / L solenoid valve 88 is off-controlled (OFF) or on-controlled (ON), the target rotational speed of the electric oil pump 70, that is, oil discharge from the electric oil pump 70. Since the amount is constant, a gap between the wall surface of the valve housing chamber and the constricted portion 73a3 of the valve body 73a is caused by a change in the pressure receiving area due to switching of the H / L solenoid valve 88 off (OFF) and on (ON). changes, towards the gap _{T oN} when H / L solenoid valve 88 is controlled to be turned on (oN) than the gap _{T oFF} when H / L solenoid valve 88 is oFF control (oFF) is small. The direction of the gap T _ON is reduced pressure on the upstream side of the regulator valve 73 is increased in the case where H / L solenoid valve 88 is controlled to be turned on (ON), the line pressure of the line oil passage 75 rises. That is, when the H / L solenoid valve 88 is turned on (ON), the line pressure of the line oil passage 75 becomes high (Hi), and when the H / L solenoid valve 88 is turned off (OFF), the line oil passage The line pressure of 75 becomes low (Lo). Thus, the line pressure of the line oil passage 75 is switched by switching the H / L solenoid valve 88 off (OFF) and on (ON). Even if the pressure and gap on the upstream side of the regulator valve 73 change, the total amount of oil per unit time passing through the constricted portion 73a3 does not change, so the flow rate of the lubricating / cooling oil passage 76 on the downstream side of the regulator valve 73 Will not change.

  Returning to FIG. 7, the brake shift valve 74 is slidably housed in the valve housing chamber and is switchable between a first operating position (right end in the figure) and a second operating position (left end in the figure). An annular supply port 74b formed on the inner peripheral surface of the substantially central portion of the valve storage chamber and communicating with the line oil passage 75; and an annular supply port 74b formed adjacent to the supply port 74b and communicating with the brake oil passage 77. A discharge port 74c, a spring 74d disposed at one end (left end in the figure) of the valve housing chamber and biasing the valve body 74a from the second operating position to the first operating position, and the other end (right end in the figure) ) And a valve body control chamber 74e for biasing the valve body 74a from the first operating position to the second operating position by selectively introducing the line pressure of the line oil passage 75 by a brake solenoid valve 83 which will be described later. Connect to drain passage And the drain port 74f, which is provided with a. That is, the supply port 74b is always in communication with the electric oil pump 70 via the line oil passage 75, and the discharge port 74c is always in communication with the hydraulic pressure regulator OC1 via the brake oil passage 77 (upstream side passage 103). ing. Hereinafter, the brake fluid passage 77 upstream of the hydraulic pressure adjustment device OC1 may be referred to as an upstream flow passage 103, and the brake fluid passage 77 downstream of the hydraulic pressure adjustment device OC1 may be referred to as a downstream flow passage 104.

  The brake solenoid valve 83 is a two-position three-port switching valve having a valve body (ball) that is operated by turning on (power supply) / off (power non-supply) of the solenoid, and is connected to a line oil passage 75. A line side port 83a, a valve side port 83b connected to the second valve body control oil passage 79 connected to the valve body control chamber 74e of the brake shift valve 74, and a drain port 83c connected to the drain passage. . The brake solenoid valve 83 is controlled to be turned on / off by the control device 8. During the on control, the line side port 83a and the valve side port 83b are shut off, and the valve side port 83b and the drain port 83c are connected to connect to the valve body control chamber. The supply of the line pressure of the line oil passage 75 to the line 74e is cut off, and at the time of off control, the line side port 83a and the valve side port 83b are connected and the valve side port 83b and the drain port 83c are cut off to cut off the valve body control chamber 74e The line pressure of the line oil passage 75 is made to act on the front end surface of the valve body 74a.

  In the brake shift valve 74, as shown in FIG. 9A, when the brake solenoid valve 83 is turned off (OFF), the line pressure of the line oil passage 75 acts on the valve body 74a through the valve body control chamber 74e, The valve element 74a moves to the second operating position on one end side (left side in the figure) of the valve accommodating chamber against the spring load of the spring 74d. When the valve body 74a is located at the second operating position, the brake shift valve 74 is closed, the valve body 74a shuts off the supply port 74b and the discharge port 74c, and communicates the discharge port 74c and the drain port 74f. The oil is discharged to the drain passage through the drain port 74f.

  On the other hand, as shown in FIG. 9B, when the brake solenoid valve 83 is on-controlled (ON), the supply of the line pressure of the line oil passage 75 to the valve body control chamber 74e is cut off, and the spring load of the spring 74d. As a result, the valve body 74a moves to the first operating position at the other end (right end in the figure) of the valve accommodating chamber. When the valve body 74a is located at the first operating position, the brake shift valve 74 is opened, the valve body 74a communicates the supply port 74b and the discharge port 74c, and shuts off the discharge port 74c and the drain port 74f. The oil is supplied from the discharge port 74c to the hydraulic pressure adjusting device OC1 via the upstream flow path 103. If the line pressure in the line oil passage 75 is high, the oil pressure in the upstream-side flow path 103 of the oil pressure adjustment device OC1 is larger than the first predetermined value, and if the line pressure in the line oil passage 75 is low, the oil pressure adjustment device OC1. If the oil pressure in the upstream flow path 103 is greater than a second predetermined value (for example, approximately zero) and less than or equal to the first predetermined value, and the line pressure in the line oil passage 75 is approximately zero, the upstream side of the hydraulic regulator OC1 The oil pressure in the flow path 103 is equal to or less than the second predetermined value.

  Thus, the brake solenoid valve 83 is closed during the ON control (power supply), and the liquid chamber circuit including the line oil passage 75 and the second valve body control oil passage 79 is closed, and the electric oil pump 70 and the valve body control chamber 74e are shut off. In addition, the liquid chamber circuit composed of the line oil passage 75 and the second valve body control oil passage 79 is opened at the time of off control (power is not supplied), and the electric oil pump 70 and the valve body control chamber 74e are brought into communication. It is arranged so that. When the brake solenoid valve 83 is turned on (power supply), the valve element 74a of the brake shift valve 74 is positioned at the first operating position by the spring 74d, and when the brake solenoid valve 83 is turned off (electricity is not supplied), the valve element control chamber The valve element 74a of the brake shift valve 74 is positioned at the second operating position by the oil stored in 74e. In the brake shift valve 74, when the valve element 74a is in the first operating position, the hydraulic circuit composed of the line oil passage 75 and the upstream passage 103 is opened so that the electric oil pump 70 and the hydraulic pressure adjusting device OC1 are in communication with each other. At the same time, when the valve body 74a is in the second operating position, the hydraulic circuit composed of the line oil passage 75 and the upstream flow passage 103 is closed, and the electric oil pump 70 and the hydraulic pressure adjusting device OC1 are shut off. Arranged.

  As described above, the hydraulic pressure adjustment device OC1 is non-electrically driven, and switches the electric oil pump 70 and the hydraulic brake 60 to the communication state or the cutoff state according to the hydraulic pressure of the upstream flow path 103.

  If the line pressure in the line oil passage 75 is substantially zero, the oil pressure in the upstream flow path 103 of the oil pressure adjusting device OC1 is equal to or lower than a second predetermined value, the pressure receiving surface 114 is seated on the bottom surface 108b of the oil pressure adjusting chamber 108, and the valve Since the body 111 is also seated on the valve seat 113, the downstream communication portion 106 and the drain opening portion 107 communicate with each other, and the downstream communication portion 106 and the drain opening portion 107 that communicate with each other and the upstream communication portion 105 are blocked. ing. Therefore, hydraulic pressure is not supplied to the downstream flow path 104 and the hydraulic brake 60 is released.

  If the line pressure in the line oil passage 75 is high, the hydraulic pressure in the upstream flow path 103 of the hydraulic pressure adjusting device OC1 becomes larger than the first predetermined value and acts on the pressure receiving surface 114 of the piston 109 as shown in FIG. 2A. Since the piston 109 is separated from the bottom surface 108b of the hydraulic pressure adjustment chamber 108 by the hydraulic pressure, and subsequently the hydraulic pressure acting on the valve body 111 from the pressure receiving surface opening 109c is larger than the urging force acting on the valve body 111 by the spring 112, the valve body 111 is separated from the valve seat 113. Thereby, since the piston columnar portion 109b of the piston 109 seals the drain opening 107, the upstream communication portion 105 and the downstream communication portion 106 communicate with each other, and the upstream communication portion 105 and the downstream communication portion communicated with each other. 106 and the drain opening 107 are blocked. Then, the oil that has passed through the gap between the valve element 111 and the valve seat 113 from the pressure receiving surface opening 109c is supplied from the downstream communication portion 106 to the working chamber S of the hydraulic brake 60 via the downstream flow path 104, and the hydraulic brake 60 is fastened. Is done.

  Subsequently, when the line pressure in the line oil passage 75 becomes low in the engaged state of the hydraulic brake 60, the hydraulic pressure in the upstream flow path 103 of the hydraulic pressure adjusting device OC1 is larger than the second predetermined value and lower than the first predetermined value. As shown in FIG. 2B, although the state in which the piston 109 is separated from the bottom surface 108b of the hydraulic pressure adjusting chamber 108 is maintained by the hydraulic pressure acting on the pressure receiving surface 114 of the piston 109, the pressure acting on the valve body 111 from the pressure receiving surface opening 109c. Since the urging force acting on the valve body 111 by the spring 112 is larger than the hydraulic pressure to be applied, the valve body 111 is seated on the valve seat 113. As a result, the piston columnar portion 109b of the piston 109 seals the drain opening 107 and the valve body 111 seals the pressure receiving surface opening 109c, so that the downstream communication portion 106 and the drain opening 107 are blocked. The downstream communication unit 106 and the upstream communication unit 105 are blocked. That is, in this state, although the line pressure of the line oil passage 75 is low, the hydraulic pressure of the downstream communication unit 106 is maintained and the engaged state of the hydraulic brake 60 can be maintained.

  In order to release the hydraulic brake 60 from this state, the line pressure in the line oil passage 75 may be made substantially zero. When the line pressure in the line oil passage 75 becomes substantially zero, as shown in FIG. 2C, the hydraulic pressure in the upstream flow path 103 of the hydraulic pressure adjusting device OC1 becomes equal to or lower than the second predetermined value. The pressure receiving surface 114 is seated on the bottom surface 108b of the hydraulic pressure adjusting chamber 108 while being seated. As a result, the downstream communication portion 106 and the drain opening portion 107 communicate with each other, and the communicated downstream communication portion 106 and drain opening portion 107 and the upstream communication portion 105 are blocked. Accordingly, the hydraulic pressure in the downstream flow path 104 is released, and the hydraulic brake 60 is released.

  In FIG. 7, reference numeral 92 is a sensor capable of detecting the temperature and pressure of oil, and reference numeral 93 is a relief valve provided in the lubrication / cooling oil passage 76. Note that a sensor for detecting the temperature of the oil may be separately provided in the oil reservoir T or the like.

  The control device 8 is a control device for performing various controls of the entire vehicle. The control device 8 includes a wheel speed sensor value from a wheel speed sensor, a brake sensor value from a vehicle brake sensor, and an accelerator pedal from an accelerator pedal sensor. In addition to the opening degree, position information of the shifter (not shown) from the shift position sensor (hereinafter referred to as shift position), the oil temperature from the sensor 92, the steering angle, the state of charge (SOC) in the battery 9 and the like are input. The On the other hand, from the control device 8, a signal for controlling the internal combustion engine 4, a signal for controlling the first and second electric motors 2A and 2B, a control signal for controlling the electric oil pump 70, an H / L solenoid valve 88 and a brake solenoid valve. A control signal for turning on / off 83 is output.

By the control device 8, the hydraulic circuit 71 and the hydraulic brake 60 of the rear wheel drive device 1 can take three states described below.
FIG. 10 shows the hydraulic circuit 71 when the hydraulic brake 60 is engaged.
The control device 8 drives the electric oil pump 70 to turn on both the H / L solenoid valve 88 and the brake solenoid valve 83. By turning on the H / L solenoid valve 88, the supply of the line pressure of the line oil passage 75 to the valve body control port 73f is cut off as shown in FIG. The line pressure of the line oil passage 75 becomes high (Hi). Further, by turning on the brake solenoid valve 83, as described in FIG. 9B, the supply of the line pressure of the line oil passage 75 to the valve body control chamber 74e is cut off, and the valve body 74a is in the first operation. The high-pressure oil is supplied from the discharge port 74c to the hydraulic pressure adjustment device OC1 through the upstream flow path 103. When high pressure oil, that is, oil with a hydraulic pressure larger than the first predetermined value is supplied to the hydraulic pressure regulator OC1, high pressure oil is supplied to the working chamber S of the hydraulic brake 60, and the hydraulic brake 60 is supplied with high pressure oil. Is in a fastened state.

FIG. 11 shows the hydraulic circuit 71 in a state where the hydraulic brake 60 is kept engaged.
After the hydraulic brake 60 is engaged, the control device 8 drives the electric oil pump 70 to turn off the H / L solenoid valve 88 and turn on the brake solenoid valve 83 in order to maintain the engagement of the hydraulic brake 60. ing. By controlling the H / L solenoid valve 88 to be off, the line pressure of the line oil passage 75 acts on the valve body 73a through the valve body control port 73f as described with reference to FIG. The line pressure in the line oil passage 75 is low (Lo). Further, by turning on the brake solenoid valve 83, as described in FIG. 9B, the supply of the line pressure of the line oil passage 75 to the valve body control chamber 74e is cut off, and the valve body 74a is in the first operation. The low-pressure oil is supplied from the discharge port 74c to the hydraulic pressure adjustment device OC1 through the upstream flow path 103. By supplying low pressure oil, that is, oil having a hydraulic pressure larger than the second predetermined value and lower than the first predetermined value, to the hydraulic pressure adjusting device OC1, the hydraulic pressure of the downstream communication unit 106 is maintained and the hydraulic clutch CL is engaged. Can be maintained.

FIG. 12 shows the hydraulic circuit 71 in a released state of the hydraulic brake 60 during traveling.
The control device 8 drives the electric oil pump 70 to turn off both the H / L solenoid valve 88 and the brake solenoid valve 83. By controlling the H / L solenoid valve 88 to be off, the line pressure of the line oil passage 75 acts on the valve body 73a through the valve body control port 73f as described with reference to FIG. The line pressure in the line oil passage 75 is low (Lo). Further, by controlling the brake solenoid valve 83 to be off, the line pressure of the line oil passage 75 acts on the valve body 74a through the valve body control chamber 74e, as described with reference to FIG. The oil is discharged from the discharge port 74c to the drain passage through the drain port 74f. Oil is discharged to the drain passage through the drain port 74f, and the hydraulic pressure in the upstream flow path 103 of the hydraulic pressure adjusting device OC1 becomes equal to or lower than the second predetermined value, so that the hydraulic pressure in the downstream flow path 104 is released and the hydraulic brake 60 Is released.

When the hydraulic brake 60 in FIGS. 10 to 12 is engaged, the electric oil pump 70 is driven and the line oil passage 75 is connected to the supply port 73b and the line pressure introduction port 73d in the engagement maintenance state and the release state (running). Since the pressure acts, the supply port 73b and the discharge port 73c are always connected, and the gap T _ON or the gap T formed by the valve housing chamber and the valve body 73a between the supply port 73b and the discharge port 73c. Oil depressurized by being _{turned off} is supplied to the lubrication / cooling oil passage 76 via the lubrication / cooling oil passage 76 at a predetermined flow rate.

FIG. 13 shows the hydraulic circuit 71 in a released state of the hydraulic brake 60 while the vehicle is stopped.
The controller 8 does not drive the electric oil pump 70 (oil pump electric motor 90) (target rotational speed = 0, the same applies hereinafter), and controls the H / L solenoid valve 88 and the brake solenoid valve 83 to be off. The point that the H / L solenoid valve 88 and the brake solenoid valve 83 are controlled to be off is the same as the release state of the hydraulic brake 60 while the vehicle is running. However, the line oil is not driven because the electric oil pump 70 is not driven when the vehicle is stopped. The line pressure of the path 75 is substantially zero. Therefore, the valve element 73a of the regulator valve 73 is positioned at the other end (right end in the figure) of the valve accommodating chamber due to the spring load of the spring 73e, and the supply port 73b and the discharge port 73c are cut off, so Oil is not supplied. Further, although the valve element 74a of the brake shift valve 74 is located at the first operating position due to the spring load of the spring 74d, no oil is supplied, so the hydraulic pressure of the upstream flow path 103 of the hydraulic pressure adjusting device OC1 is equal to or less than a second predetermined value. As a result, the hydraulic pressure in the downstream flow path 104 is released, and the hydraulic brake 60 is in a released state.

  As described above, the control device 8 controls the driving / non-driving of the electric oil pump 70 and the on / off of the H / L solenoid valve 88 and the brake solenoid valve 83 to thereby engage, maintain, or maintain the hydraulic brake 60. The power transmission path between the first and second electric motors 2A, 2B and the rear wheel Wr can be switched between a connected state and a disconnected state.

  14 to 18 show speed collinear charts in the respective states of the rear wheel drive device 1. The LMOT is connected to the first electric motor 2A, the RMOT is connected to the second electric motor 2B, and the left S and C are connected to the first electric motor 2A. The sun gear 21A of the first planetary gear speed reducer 12A, the planetary carrier 23A of the first planetary gear speed reducer 12A, and S and C on the right side are the sun gear 21B and the second planetary gear type of the second planetary gear speed reducer 12B, respectively. The planetary carriers 23B, R of the speed reducer 12B are the ring gears 24A, 24B, BRK of the first and second planetary gear speed reducers 12A, 12B, the hydraulic brake 60, and the OWC is the one-way clutch 50. In the following description, the rotation direction of the sun gears 21A and 21B when the vehicle is advanced by the first and second electric motors 2A and 2B is assumed to be the forward direction. Also, in the figure, from the stationary state, the upper direction is forward rotation and the lower side is reverse direction rotation, and the arrows indicate forward torque and downward direction indicates reverse torque.

  While the vehicle is stopped, neither the front wheel drive device 6 nor the rear wheel drive device 1 is driven. Accordingly, as shown in FIG. 14, the first and second electric motors 2A and 2B of the rear wheel drive device 1 are stopped, and the axles 10A and 10B are also stopped. Therefore, torque acts on any of the elements. Not. At this time, as described with reference to FIG. 13, the control device 8 does not drive the electric oil pump 70 and controls the H / L solenoid valve 88 and the brake solenoid valve 83 to be off, thereby releasing the hydraulic brake 60. Yes. The one-way clutch 50 is not engaged because the first and second electric motors 2A and 2B are not driven (OFF).

  Then, after the key position is turned ON, the rear wheel drive device 1 performs the rear wheel drive at the forward low vehicle speed with good motor efficiency such as EV start and EV cruise. As shown in FIG. 15, when the first and second electric motors 2A and 2B are power-driven so as to rotate in the forward direction, forward torque is applied to the sun gears 21A and 21B. At this time, as described above, the one-way clutch 50 is engaged and the ring gears 24A and 24B are locked. As a result, the planetary carriers 23A and 23B rotate in the forward direction and travel forward. In addition, traveling resistance from the axles 10A and 10B acts on the planetary carriers 23A and 23B in the reverse direction. Thus, when the vehicle 3 is started, the one-way clutch 50 is mechanically engaged and the ring gears 24A and 24B are locked by increasing the torque of the first and second electric motors 2A and 2B.

  At this time, as described with reference to FIG. 10, the control device 8 drives the electric oil pump 70, controls the H / L solenoid valve 88 on, and controls the brake solenoid valve 83 to turn on the hydraulic brake 60. Conclude. Further, after the hydraulic brake 60 is engaged, the H / L solenoid valve 88 is turned off and the brake solenoid valve 83 is turned on, as described with reference to FIG.

  Thus, when the forward rotational power of the first and second electric motors 2A and 2B is input to the rear wheel Wr, the one-way clutch 50 is engaged, and power can be transmitted only by the one-way clutch 50. However, the hydraulic brake 60 provided in parallel with the one-way clutch 50 is also in the engaged state, and the first and second electric motors 2A, 2B and the rear wheel Wr are connected, so that the first and second electric motors 2A are connected. Even when the input of forward rotational power from the 2B side temporarily decreases and the one-way clutch 50 becomes disengaged, the first and second motors 2A, 2B and the rear wheel Wr side It can suppress that power transmission becomes impossible. Further, it is not necessary to control the number of revolutions for connecting the first and second electric motors 2A, 2B and the rear wheel Wr when shifting to deceleration regeneration, which will be described later.

  When starting the vehicle 3 from such a stop, at the time of starting the electric oil pump 70 for switching the oil pump electric motor 90 from the stop state to the driving state, simultaneously with the power supply to the oil pump electric motor 90 or for the oil pump It is preferable to supply power (ON control) to the brake solenoid valve 83 before supplying power to the electric motor 90. Thereby, before the line pressure of the line oil passage 75 rises, the supply of the line pressure of the line oil passage 75 to the valve body control chamber 74e is cut off, so that the brake shift valve 74 has the valve body 74a in the first operating position. Accordingly, the brake shift valve 74 is also kept open. Therefore, the line pressure of the line oil passage 75 immediately acts on the hydraulic pressure adjusting device OC1 via the upstream side passage 103.

  When the vehicle speed increases from the forward low vehicle speed travel to the forward vehicle speed travel with good engine efficiency, the rear wheel drive by the rear wheel drive device 1 changes to the front wheel drive by the front wheel drive device 6. As shown in FIG. 16, when the power driving of the first and second electric motors 2A and 2B is stopped, the planetary carriers 23A and 23B are acted on by forward torque from the axles 10A and 10B to travel forward. As described above, the one-way clutch 50 is disengaged. Also at this time, as described with reference to FIG. 11, the control device 8 drives the hydraulic oil pump 70 by driving the electric oil pump 70, turning off the H / L solenoid valve 88, and turning on the brake solenoid valve 83. The fastening state is maintained.

  When the first and second electric motors 2A, 2B are regeneratively driven from the state of FIG. 15 or FIG. 16, as shown in FIG. 17, the planetary carriers 23A, 23B are forwardly driven to continue traveling forward from the axles 10A, 10B. Therefore, the one-way clutch 50 is disengaged as described above.

  Also at this time, as described with reference to FIG. 11, the control device 8 drives the hydraulic oil pump 70 by driving the electric oil pump 70, turning off the H / L solenoid valve 88, and turning on the brake solenoid valve 83. The fastening state is maintained. Accordingly, the ring gears 24A and 24B are fixed, and the regenerative driving torque in the reverse direction acts on the sun gears 21A and 21B, and the first and second electric motors 2A and 2B perform decelerated regeneration. Thus, when the forward rotational power on the rear wheel Wr side is input to the first and second electric motors 2A, 2B, the one-way clutch 50 is disengaged, and power cannot be transmitted only by the one-way clutch 50. However, the hydraulic brake 60 provided in parallel with the one-way clutch 50 is fastened, and the first and second electric motors 2A, 2B and the rear wheel Wr are in a connected state so that power can be transmitted. In this state, by controlling the first and second electric motors 2A and 2B to the regenerative drive state, the energy of the vehicle can be regenerated.

  Subsequently, at the time of acceleration, the four-wheel drive of the front wheel drive device 6 and the rear wheel drive device 1 is performed, and the rear wheel drive device 1 is in the same state as at the forward low vehicle speed shown in FIG. The hydraulic circuit 71 is also in the state shown in FIG.

  At the forward high vehicle speed, the front wheel drive device 6 performs front wheel drive, but as shown in FIG. 18, when the first and second motors 2A, 2B stop the power running drive, the planetary carriers 23A, 23B have axles 10A, 10B. Since the forward torque that tries to travel forward is applied, the one-way clutch 50 is disengaged as described above. At this time, the rotation loss of the sun gears 21A and 21B and the first and second electric motors 2A and 2B is input as resistance to the sun gears 21A and 21B, and the rotation loss of the ring gears 24A and 24B is input as resistance to the ring gears 24A and 24B. Is done.

  At this time, the control device 8 releases the hydraulic brake 60 by driving the electric oil pump 70 and controlling both the H / L solenoid valve 88 and the brake solenoid valve 83 to be off as described with reference to FIG. . By controlling the hydraulic brake 60 to the released state, the ring gears 24A and 24B are allowed to freely rotate, and the first and second electric motors 2A and 2B and the rear wheel Wr are cut off and cannot transmit power. It becomes a state. Accordingly, the accompanying rotation of the first and second electric motors 2A and 2B is prevented, and the first and second electric motors 2A and 2B are prevented from over-rotating at a high vehicle speed by the front wheel drive device 6.

  At the time of reverse travel, as shown in FIG. 19, when the first and second electric motors 2A, 2B are driven in reverse power running, reverse torque is applied to the sun gears 21A, 21B. At this time, as described above, the one-way clutch 50 is disengaged.

  At this time, as described with reference to FIG. 10, the control device 8 drives the electric oil pump 70 to turn on the H / L solenoid valve 88 and turn on the brake solenoid valve 83 to engage the hydraulic brake 60. To do. Further, after the hydraulic brake 60 is engaged, the H / L solenoid valve 88 is turned off and the brake solenoid valve 83 is turned on, as described with reference to FIG. Accordingly, the ring gears 24A and 24B are locked, and the planetary carriers 23A and 23B rotate in the reverse direction to travel backward. Note that traveling resistance from the axles 10A and 10B acts in the forward direction on the planetary carriers 23A and 23B. Thus, when the reverse torque on the first and second electric motors 2A, 2B side is input to the rear wheel Wr, the one-way clutch 50 is disengaged, and power transmission is impossible only by the one-way clutch 50. However, the hydraulic brake 60 provided in parallel with the one-way clutch 50 is fastened and the first and second motors 2A, 2B and the rear wheel Wr can be connected to enable transmission of power. The vehicle 3 can be moved backward by the reverse power running torque of the first and second electric motors 2A, 2B.

  Thus, the rear wheel drive device 1 is configured so that the traveling state of the vehicle, in other words, whether the rotation direction of the first and second motors 2A, 2B is the forward direction or the reverse direction, and the first and second motors 2A, 2B side. Engagement / release of the hydraulic brake 60 is controlled according to which power is input from the rear wheel Wr side.

  FIG. 20 shows a one-way clutch when the vehicle is stopped, EV start → EV acceleration → ENG acceleration → deceleration regeneration → medium speed ENG cruise → ENG + EV acceleration → high speed ENG cruise → deceleration regeneration → stop → reverse → stop. 50 is a timing chart of 50 (OWC) and hydraulic brake 60 (BRK).

  First, the one-way clutch 50 is disengaged (OFF) and the hydraulic brake 60 is released until the key position is turned ON and the shift position is changed from the P range to the D range and the accelerator pedal is depressed. OFF) state is maintained. From there, when the accelerator pedal is depressed, EV start and EV acceleration are performed by the rear wheel drive device 1 in the rear wheel drive (RWD). At this time, the one-way clutch 50 is engaged (ON), and the hydraulic brake 60 is It is concluded. When the vehicle speed changes from the low vehicle speed range to the medium vehicle speed range and changes from the rear wheel drive to the front wheel drive, ENG traveling (FWD) is performed by the internal combustion engine 4. At this time, the one-way clutch 50 is disengaged (OFF), and the hydraulic brake 60 is maintained as it is (engaged state). During deceleration regeneration such as when the brake is stepped on, the one-way clutch 50 remains disengaged (OFF) and the hydraulic brake 60 is maintained as it is (engaged state). During a medium speed cruise by the internal combustion engine 4, the state is the same as the above-described ENG traveling. Subsequently, when the accelerator pedal is further depressed to change from front wheel drive to four wheel drive (AWD), the one-way clutch 50 is engaged (ON) again. When the vehicle speed reaches from the middle vehicle speed range to the high vehicle speed range, ENG traveling (FWD) by the internal combustion engine 4 is performed again. At this time, the one-way clutch 50 is disengaged (OFF), the hydraulic brake 60 is released (OFF), and the first and second electric motors 2A and 2B are stopped. And at the time of deceleration regeneration, it will be in the state similar to the time of the deceleration regeneration mentioned above. When the vehicle stops, the one-way clutch 50 is disengaged (OFF), and the hydraulic brake 60 is released (OFF).

  Subsequently, during reverse travel, the one-way clutch 50 remains disengaged (OFF) and the hydraulic brake 60 is engaged (ON). When the vehicle stops, the one-way clutch 50 is disengaged (OFF), and the hydraulic brake 60 is released (OFF).

  As described above, according to the present embodiment, the hydraulic pressure adjusting device OC1 is connected to the electric oil pump 70 and the hydraulic pressure when the hydraulic pressure in the upstream flow path 103 becomes equal to or lower than the first predetermined value when the hydraulic brake 60 is engaged. The engaged state of the hydraulic brake 60 can be maintained by bringing the brake 60 into a disconnected state. Accordingly, since it is not necessary to supply power to the H / L solenoid valve 88 in order to maintain the engagement of the hydraulic brake 60, the power consumption of the H / L solenoid valve 88 can be reduced.

  Further, when no power is supplied to the brake solenoid valve 83, the liquid chamber circuit including the line oil passage 75 and the second valve body control oil passage 79 is opened, and the electric oil pump 70 and the valve body control chamber 74e are brought into communication with each other. If the electric oil pump 70 is driven, the brake shift valve 74 is positioned at the second operating position against the spring 74d, so that the hydraulic circuit comprising the line oil passage 75 and the brake oil passage 77 is provided. The electric oil pump 70 and the hydraulic brake 60 are shut off by being closed. Therefore, in an electrically driven device, a failure that can not be started from a stopped state (power non-supply state) is more likely to occur than a failure that cannot be stopped from an activated state. Even in the case where a failure that makes it impossible to start from the stop state occurs, the safety is high because the hydraulic brake 60 is released.

  Further, when no power is supplied to the brake solenoid valve 83, the liquid chamber circuit including the line oil passage 75 and the second valve body control oil passage 79 is opened, and the electric oil pump 70 and the valve body control chamber 74e are brought into communication with each other. When the electric oil pump 70 is stopped, the brake shift valve 74 has the valve element 74a located at the first operating position by the spring 74d, and the hydraulic circuit composed of the line oil passage 75 and the brake oil passage 77 is opened to be electrically operated. The oil pump 70 and the hydraulic brake 60 are brought into communication. Therefore, unless the hydraulic pressure is supplied to the valve body control chamber 74e when the electric oil pump 70 is started from this state, the hydraulic pressure generated in the hydraulic circuit including the line oil passage 75 and the brake oil passage 77 is immediately supplied to the hydraulic brake 60. Can be added.

  Further, the hydraulic pressure adjusting device OC1 can release the hydraulic brake 60 by releasing the hydraulic pressure in the downstream side channel 104 when the upstream side channel 103 is below the second predetermined value.

  Further, when the hydraulic pressure in the upstream flow path 103 is larger than the second predetermined value, the valve body 111 is separated from the valve seat 113, whereby the electric oil pump 70 and the hydraulic pressure adjusting device OC1 can be brought into communication. it can. In addition, when the hydraulic brake 60 is engaged, the valve body 111 is seated on the valve seat 113 when the hydraulic pressure in the upstream flow path 103 is greater than the second predetermined value and less than or equal to the first predetermined value. The electric oil pump 70 and the hydraulic pressure adjusting device OC1 can be in a cut-off state.

  Further, when the fluid pressure in the upstream channel 103 is equal to or lower than the second predetermined value, the fluid pressure in the downstream channel 104 can be released by communicating the downstream communication unit 106 and the drain opening 107. it can.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
Although the hydraulic drive type wet multi-plate brake is illustrated as the connection / disconnection means, the invention is not limited to this, and a dry multi-plate brake or a brake using pressure of liquid other than oil may be used.
Further, the drive device can be used in transportation equipment such as a vehicle, an aircraft, and a ship. In the following embodiments, a case where the drive device is used in a vehicle will be described as an example.

1 Rear wheel drive device (drive device)
2A 1st electric motor (drive source)
2B Second electric motor (drive source)
3 Vehicle (Transportation)
60 Hydraulic brake (connection / disconnection means)
74 Brake shift valve (first switching valve)
74a Valve body 74e Valve body control chamber (liquid chamber)
74d Spring (return means)
75 Line oil passage (hydraulic pressure circuit)
79 Second valve body control oil passage (liquid chamber circuit)
83 Brake solenoid valve (3rd switching valve)
100 Drive device 102 Electric motor (drive source)
103 upstream flow path 104 downstream flow path 105 upstream communication section 106 downstream communication section 111 valve body 113 valve seat 107 drain opening 109 piston 114 pressure receiving surface CL hydraulic clutch (connection / disconnection means)
EOP Electric oil pump (hydraulic pressure supply means)
OC1 Hydraulic adjustment device (hydraulic pressure adjustment device)
OC2 Hydraulic adjustment device (hydraulic pressure adjustment device)
W wheel (driven part)
Wr Rear wheel (driven part)

Claims (8)

A driving source;
A driven part that is driven by the drive source and propels the transportation;
A hydraulically driven connection / disconnection means provided on a power transmission path between the drive source and the driven part, and releasing or fastening the power transmission path to be in a cut-off state or a connection state;
Hydraulic supply means for supplying hydraulic pressure to the connecting and disconnecting means;
A hydraulic pressure adjusting device connected to the hydraulic pressure supply means via an upstream flow path and connected to the connecting / disconnecting means via a downstream flow path;
The hydraulic pressure adjusting device is a non-electrically driven type, and is a driving device that switches the hydraulic pressure supply means and the connecting / disconnecting means to a communication state or a cutoff state according to the hydraulic pressure of the upstream flow path. And
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream flow path is greater than a first predetermined value, the hydraulic pressure supply means and the connection / disconnection means are brought into communication with each other to fasten the connection / disconnection means,
In the engaged state of the connection / disconnection means, the hydraulic pressure supply means and the connection / disconnection means are disconnected when the hydraulic pressure in the upstream-side flow path becomes equal to or lower than the first predetermined value. A drive device that maintains the fastening state of the contact means. The drive device according to claim 1,
The hydraulic pressure adjusting device adjusts the hydraulic pressure of the downstream flow path when the hydraulic pressure of the upstream flow path is equal to or lower than a second predetermined value smaller than the first predetermined value in the engaged state of the connection / disconnection means. A drive device that releases the connection / disconnection means by opening. The drive device according to claim 2,
The hydraulic pressure adjusting device includes an upstream communication portion connected to the upstream flow channel, a downstream communication portion connected to the downstream flow channel, a valve body, and a valve seat.
The valve body is provided so as to be seated on the valve seat from the downstream communication portion side so as to close the upstream communication portion,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream flow path is greater than the first predetermined value, the valve body is separated from the valve seat so that the hydraulic pressure supply means and the connection / disconnection means are in communication with each other,
The valve element is seated on the valve seat when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value in the engaged state of the connection / disconnection means. Then, the drive device that puts the hydraulic pressure supply means and the connection / disconnection means in a disconnected state. The drive device according to claim 3,
The fluid pressure adjusting device further includes a drain opening for releasing the fluid pressure, and a piston having a communicating portion,
The piston is provided with a pressure receiving surface on the upstream side of the communication portion, and the valve seat is provided on the downstream side of the pressure receiving surface,
The hydraulic pressure adjusting device is
Due to the hydraulic pressure acting on the pressure receiving surface when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value, the piston opens from the downstream communication portion to the drain opening. Shut off
The drive device, wherein the piston communicates the downstream communication portion and the drain opening when the hydraulic pressure in the upstream flow path is equal to or less than the second predetermined value. A driving source;
A driven part that is driven by the drive source and propels the transportation;
A hydraulically driven connection / disconnection means provided on a power transmission path between the drive source and the driven part, and releasing or fastening the power transmission path to be in a cut-off state or a connection state;
A hydraulic pressure supply means for supplying a hydraulic pressure to the connection / disconnection means,
The drive device is capable of adjusting a hydraulic pressure of the hydraulic pressure circuit, a hydraulic pressure circuit communicating the hydraulic pressure supply means and the connecting / disconnecting means, a first switching valve disposed on the hydraulic pressure circuit, and the hydraulic pressure circuit. A second switching valve,
The first switching valve communicates with a valve body that can be switched between a first operating position and a second operating position, and the hydraulic pressure supply means, and moves the valve body from the first operating position to the second operating position. A liquid chamber that houses a hydraulic medium that urges in the direction, and a return means that urges the valve body from the second operating position toward the first operating position.
The second switching valve is electrically driven, and controls the hydraulic pressure of the hydraulic circuit to be greater than a first predetermined value when power is supplied, and sets the hydraulic pressure of the hydraulic circuit to a first value when power is not supplied. 1 Control to be below a predetermined value,
The drive device further includes an electrically driven third switching valve that is disposed on a fluid chamber circuit that communicates the fluid pressure supply means and the fluid chamber, and that is operated by electric power,
The third switching valve closes the liquid chamber circuit when power is supplied to shut off the liquid pressure supply means and the liquid chamber, and opens the liquid chamber circuit when power is not supplied. The pressure supply means and the liquid chamber are disposed so as to communicate with each other,
A hydraulic pressure adjusting device is provided between the third switching valve and the connection / disconnection means,
The first switching valve is configured such that when the valve body is in the first operating position, the hydraulic circuit is opened so that the hydraulic pressure supply means and the hydraulic pressure adjusting device are in communication with each other, and the valve body Is disposed so that the hydraulic pressure circuit is closed when the second operating position, and the hydraulic pressure supply means and the hydraulic pressure adjusting device are cut off,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream-side flow path of the hydraulic pressure adjusting device is greater than the first predetermined value, the connecting / disconnecting means is fastened by bringing the hydraulic pressure supply means and the connecting / disconnecting means into communication. ,
In the engaged state of the connection / disconnection means, the hydraulic pressure supply means and the connection / disconnection means are disconnected when the hydraulic pressure in the upstream-side flow path becomes equal to or lower than the first predetermined value. A drive device that maintains the fastening state of the contact means. The drive device according to claim 5,
The hydraulic pressure adjusting device opens the hydraulic pressure in the downstream flow channel of the hydraulic pressure adjusting device when the hydraulic pressure in the upstream flow channel is equal to or lower than a second predetermined value that is smaller than the first predetermined value. A drive device for releasing the connecting / disconnecting means. The drive device according to claim 6,
The hydraulic pressure adjusting device includes an upstream communication portion connected to the upstream flow channel, a downstream communication portion connected to the downstream flow channel, a valve body, and a valve seat.
The valve body is provided so as to be seated on the valve seat from the downstream communication portion side so as to close the upstream communication portion,
The hydraulic pressure adjusting device is
When the hydraulic pressure in the upstream flow path is larger than the first predetermined value, the valve body is separated from the valve seat, so that the hydraulic pressure supply means and the connection / disconnection means are in communication with each other,
The valve element is seated on the valve seat when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value in the engaged state of the connection / disconnection means. The drive device that puts the hydraulic pressure supply means and the connection / disconnection means in a disconnected state. The drive device according to claim 7,
The fluid pressure adjusting device further includes a drain opening for releasing the fluid pressure, and a piston having a communicating portion,
The piston is provided with a pressure receiving surface on the upstream side of the communication portion, and the valve seat is provided on the downstream side of the pressure receiving surface,
The hydraulic pressure adjusting device is
Due to the hydraulic pressure acting on the pressure receiving surface when the hydraulic pressure in the upstream flow path is greater than the second predetermined value and less than or equal to the first predetermined value, the piston is removed from the downstream communication portion by the drain. Block the opening,
The drive device, wherein the piston communicates the downstream communication portion and the drain opening when the hydraulic pressure in the upstream flow path is equal to or less than the second predetermined value.

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