JPH0567465B2 - - Google Patents

Description

[Detailed Description of the Invention] A. Purpose of the Invention (1) Industrial Field of Application The present invention is characterized in that a power unit is connected to one of the front and rear axles, and the other axle has a high relative rotational speed. The present invention relates to a four-wheel drive vehicle that is connected to a power unit via a torque transmission mechanism that increases the amount of torque transmitted as the torque increases.

(2) Prior Art Conventionally, in such four-wheel drive vehicles, each wheel is generally equipped with a brake.

(3) Problems to be solved by the invention By the way, in the above vehicle, the front and rear axles are almost always connected rigidly, so if the brake hydraulic pressure becomes excessive during sudden braking, all the wheels will lock at the same time. Therefore, compared to a front-wheel or rear-wheel drive vehicle, stability during braking is improved, but stability against external disturbances and loss of steering performance cannot be resolved. Therefore, it is desirable to provide the brake device with an anti-lock function.

However, anti-lock brakes basically control the brake torque for each wheel or each axle to maintain the slip rate of each wheel around an appropriate value, and the speed of each wheel or each axle is It is necessary to be able to vary independently. On the other hand, in vehicles where the front and rear axles are almost rigidly connected, the front and rear wheels interfere with each other, so
Appropriate control cannot be obtained by performing anti-lock control on each brake in a wheel equipped with a brake as in the past.

On the other hand, when the front and rear axles are almost rigidly connected, if an appropriate slip rate is given to the wheels on one axle, the slip rate of the wheels on the other axle will inevitably be approximately the appropriate value. be.

Therefore, the above-mentioned problems can be solved by installing brakes only on the front wheels to obtain braking force for all wheels and performing anti-lock control on those brakes. We are proposing a four-wheel drive configuration.

However, if only the front wheel brake is responsible for braking all wheels, the load on the front wheel brake will be large, and it may be difficult to increase its capacity due to space constraints.

The present invention has been made in view of the above circumstances.A brake is also installed on the rear wheel in order to reduce the burden on the front wheel brake, and the anti-lock control of the rear wheel brake minimizes interference from the rear wheel to the front wheel. The purpose of the present invention is to provide a four-wheel drive vehicle that can be made smaller.

B. Structure of the Invention (1) Means for Solving the Problems According to the present invention, brakes are attached to the wheels of both axles, and the brake hydraulic system that controls the hydraulic pressure of each brake has a mechanism that prevents the wheels from being locked. An anti-lock control device is attached that controls the brake hydraulic pressure to be released when the vehicle is about to enter the vehicle. In the rear wheel control section, the reference value for determining whether the wheels are likely to enter a locked state is set more gently than in the front wheel control section.

(2) Effect The slip rate of the rear wheels is smaller than that of the front wheels because the reference value is set gradually smaller in the rear wheel control section, and interference from the rear wheels to the front wheels can be suppressed to a small level.

(3) Embodiment An embodiment of the present invention will be explained below with reference to the drawings. First, in Fig. 1, a pair of left and right front wheels are shown.
Wfl, Wfr and a pair of left and right rear wheels Wrl, Wrr are suspended at the front and rear of a vehicle body (not shown), respectively.

A pair of front axles Afl, Afr connected to left and right front wheels Wfl, Wfr, respectively, are connected to each other via a front differential Df, and a pair of rear axles Arl, Arr connected to left and right rear wheels Wrl, Wrr, respectively. rear differential
They are interconnected via Dr. Front differential Df
A power unit P including an engine and a transmission is connected to the input section of the engine. Also rear differential
The rear propulsion shaft Pr is connected to the input part of Dr. This rear propulsion shaft Pr is coaxially connected to the front propulsion shaft Pf via a viscose clutch 1 serving as a torque transmission mechanism, and the driving force of the power unit P is transmitted to the front propulsion shaft Pf.

A viscose clutch 1 has a sealed oil chamber 4 defined between a clutch outer 2 and a clutch inner 3 that are rotatable relative to each other, and a high viscosity oil and a small amount of air that allows thermal expansion of the high viscosity oil are sealed. and a plurality of outer clutch plates 5 and a clutch inner 3 spline-coupled to the clutch outer 2.
A plurality of inner clutch plates 6 are spline-coupled to each other and arranged in an overlapping manner. In addition, each plate 5, 6 is provided with an opening (not shown) that allows oil to flow, and the clutch outer 2 is integrated with the forward propulsion shaft Pf, and the clutch inner 3 is integrated with the rear propulsion shaft Pr.

In this viscose clutch 1, when relative rotation occurs between clutch outer 2 and clutch inner 3, both clutch plates 5 and 6 rotate relative to each other while shearing high viscosity oil, and torque is viscous transmitted between both clutch plates 5 and 6. will be carried out. Furthermore, when the relative rotational speed increases further, a complicated temperature gradient occurs in both clutch plates 5 and 6 due to the increase in oil temperature, and due to the synergistic effect of the strain caused by this and the pressure increase in the sealed oil chamber 4, A frictionally engaged portion or a portion with an extremely small gap is formed between the two clutch plates 5 and 6, and as a result, torque is frictionally transmitted between the clutch outer 2 and the clutch inner 3.

According to such a viscose clutch 1, the front propulsion shaft Pf and the rear propulsion shaft Pr, that is, the front axles Afl, Afr and the rear axles Arl, Arr, are always almost rigidly connected, Front wheel Wfl,
Wfr and rear wheels Wrl and Wrr interfere with each other.

Brakes Bfl and Bfr are attached to the front wheels Wfl and Wfr, and brakes Brl and Brr of relatively small capacity are attached to the rear wheels Wrl and Wrr.

In Figure 2, each brake Bfl, Bfr, Brl,
The brake hydraulic system 7 that controls the hydraulic pressure of Brr has a tandem master cylinder 8 having a pair of output ports 8a and 8b, and adjusts the hydraulic pressure supplied from one output port 8a to adjust the hydraulic pressure supplied from the left front wheel brake Bfl and the right rear wheel. Modulator leading to wheel brake Brr
Mfl, Mrr, and a modulator Mfr that adjusts the hydraulic pressure supplied from the other output port 8b and guides it to the right front wheel brake Bfr and the left rear wheel brake Brr,
Equipped with Mrl. This brake hydraulic system 7 includes
An anti-lock control device 9 is provided to control the operation of modulators Mfl, Mfr, Mrl and Mrr in order to prevent the wheels from entering a locked state.

The anti-lock control device 9 includes a front wheel control section 9a that individually controls modulators Mfl and Mfr for front wheels Wfl and Wfr, and modulators Mrl and Mfr for rear wheels Wrl and Wrr.
A detector 10 has a rear wheel control section 9b that simultaneously controls Mrr, and detects the wheel speed of the front wheels Wfl and Wfr.
Signals from the rear wheels Wrl and 10r are input to the front wheel control section 9a, and signals from detectors 11l and 11r for detecting the wheel speeds of the rear wheels Wrl and Wrr are input to the rear wheel control section 9b.

Next, referring also to FIG. 3, the front wheel control section 9a
However, since the parts corresponding to one modulator Mfl and the parts corresponding to the other modulator Mfr are basically the same, the parts related to one modulator Mfl will be explained below. The subscript 1 will be used for explanation, and the parts related to the other modulator Mfr will only be illustrated using the suffix r.

In order to determine whether the wheels are about to enter a lock state, the wheel speed V _W detected by the detector 10l is input to the inverting terminal of the first comparator 13l, and is also input to the arithmetic circuit 12l.
The wheel acceleration V _W obtained by this calculation circuit 12l is applied to the inverting terminal of the second comparator 14l and the third comparator 1
The signals are respectively input to the non-inverting terminals of 5l. The first comparator 13l compares the reference wheel speed V _R input to its non-inverting terminal with the wheel speed V _W , and when V _R > V _W , the signal λ for relaxing the control hydraulic pressure is set at the first comparator 13l. 1 comparator 13l. In addition, the second comparator 14l compares the reference wheel deceleration -V・_WO input to the non-inverting terminal with the wheel acceleration V・_W , and when -V・_WO >V・_W , , a signal β for relaxing the brake oil pressure is output from the second comparator 14l. Furthermore, the third comparator 15l compares the reference wheel acceleration +V・_WO input to the inversion terminal with the wheel acceleration V・_W , and when V・_W >+V・_WO , the third comparison A signal α is output from the device 15l. This signal α is used to determine whether the wheel speed V _W is increasing, and the timing to continue loosening the braking oil pressure is determined based on this signal α.

The output terminal of the first comparator 13l is AND gate 1
6l, and is also connected to the input terminal of OR gate 17l. Further, the output terminal of the second comparator 14l is connected to the AND gate 16l and
It is connected to the input terminal of OR gate 17l. Furthermore, the output terminal of the third comparator 15l is the OR gate 17
It is connected to the input terminal of l.

The output terminal of AND gate 16l is inverted and
It is connected to the input terminals of AND gates 18l and 19l, and is also connected to the output terminal 20l. Also, the output terminal of OR gate 17l is AND gate 18
The AND gate 18l is connected to the input terminal of the AND gate 18l.
The output terminal is connected to the output terminal 22l and inverted to the input terminal of the AND gate 19l. Further, the output terminal of the AND gate 19l is connected to the output terminal 21l.

In the front wheel control section 9b configured in this way, a signal for reducing the braking pressure is output from the output terminals 20l, 20r, a signal for increasing the braking pressure is output from the output terminals 21l, 21r, and a signal for increasing the braking pressure is output from the output terminals 22l, 20r.
2r outputs a signal to keep the braking pressure constant. One modulator Mfl has output terminal 20
Operates in response to signals from l, 21l, 22l,
The other modulator Mfr has output terminals 20r and 21
It operates in response to signals from brakes Bfl and 22r, whereby anti-lock control of both brakes Bfl and Bfr is performed individually.

In FIG. 4, the configuration of the rear wheel control section 9b will be explained. This rear wheel control section 9b is similar in configuration to the front wheel control section 9a, and the front wheel control section 9
The parts corresponding to a are only illustrated with the same reference numerals without the suffixes l and r.

Particularly noteworthy in the rear wheel control section 9b is the detector 1
The wheel speeds detected at 1l and 11r are input to the low select circuit 23, and the lower wheel speed selected by the low select circuit 23 is input to the first comparator 13 and the calculator 12. .
That is, among the left and right rear wheels Wrl and Wrr, anti-lock control is performed on the wheel that is more likely to lock, that is, the wheel that has a lower wheel speed, and the control signals output from the output terminals 20, 21, and 22 The operation of both modulators Mrl and Mrr is controlled simultaneously.

Furthermore, in the rear wheel control section 9b, the reference value for determining whether or not the wheels are likely to antilock is set more gently than in the front wheel control section 9a. That is, the reference wheel speed V _R ' input to the non-inverting terminal of the first comparator 13 is larger than the reference wheel speed V _R in the front wheel control section 9a (V _R '>V _R ).
is set, and when V _R ′＞V _W, the first
The comparator 13 outputs a signal λ' for relaxing the braking oil pressure. Further, the reference wheel deceleration -V· _WO ' input to the non-inverting terminal of the second comparator 14 is determined by the front wheel control unit 9a.
The reference wheel deceleration at −V・_WO is larger than (−
V・_WO ′＞−V・_WO ) is set, and −V・_WO ′＞V
- When the torque is _W , the second comparator 14 outputs a signal β' for relaxing the braking oil pressure.

Next, to explain the operation of this embodiment, each brake Bfl,
Bfr: Supplies brake hydraulic pressure to Brr, Brr, and each wheel
When applying braking force to Wfl, Wfr; Wrl, Wrr,
Assume that the brake oil pressure becomes excessive. At this time, the rear wheel control section 9b of the antilock control device 9
In this case, the reference value for determining whether or not the rear wheels Wrl and Wrr are likely to lock up is gentler than that of the front wheels, so the slip rate of the rear wheels Wrl and Wrr is suppressed to be smaller than that of the front wheels. i.e. rear wheel
The brake torque of Wrl, Wrr becomes smaller due to the rear wheel drive force on the road surface, and the brake torque of the rear wheels Wrl, Wrr changes to the front wheel Wfl,
Since interference with Wfr can be kept small,
It becomes possible to perform good anti-lock control.

Further, since the front wheel control brake 9a individually controls the front wheel modulators Mfl and Mfr, excellent effects can be obtained in terms of braking distance and driving stability.
That is, front wheels Wfl, Wfr and rear wheels Wrl, Wrr
In four-wheel drive vehicles, where the front wheels are almost rigidly connected,
The control of Wfl, Wfr affects the rear wheels Wrl, Wrr, so if the high select method is used to simultaneously control the modulators Mfl, Mfr based on the higher of the front wheel speeds, the front wheels Wfl, Wfr
There is a possibility that one of the rear wheels may become locked, and the effect will extend to both rear wheels Wrl and Wrr, causing the rear wheels Wrl and Wrr to become locked.
Wrr slips, resulting in poor driving stability. In addition, the front wheels Wfl and Wfr with high load distribution
Then, both brakes Bfl, based on the front wheel speed on the low speed side,
It is clear that braking distance will be extended by adopting the low select method that simultaneously controls BFR.

In the above embodiment, the rear wheel side modulator
Although Mrl and Mrr are controlled simultaneously by the low selection method, they may be controlled individually.

C. Effects of the Invention As described above, according to the present invention, brakes are installed on the front and rear wheels, and the anti-lock control of the brake on the rear wheel side is relaxed so that the reference value for determining whether the wheels are likely to lock is relaxed. As a result, interference from the rear wheels to the front wheels can be kept to a minimum, and even though the front wheels and rear wheels are connected almost rigidly, it is possible to perform appropriate anti-lock control. This makes it possible to reduce the burden on the front brakes.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, in which Fig. 1 is a schematic diagram of the drive system, Fig. 2 is a schematic diagram of the brake system, Fig. 3 is a schematic diagram of the front wheel control section, and Fig. 4 is a schematic diagram of the rear wheel control section. It is a schematic diagram of a wheel control part. 1... Viscose clutch as a torque transmission mechanism, 7... Brake hydraulic system, 9... Anti-lock control device, 9a... Front wheel control section, 9b... Rear wheel control section, Afl, Afr, Afr, Arl, Arr. ……axle,
Bfl, Bfr...Brake, P...Power unit,
Wfl, Wfr, Wrl, Wrr...wheels.

Claims (1)

[Claims] 1 A power unit is connected to either the front or rear axle, and the other axle is connected to the power unit via a torque transmission mechanism that transmits a larger amount of torque as the relative rotational speed increases. In connected four-wheel drive vehicles, brakes are attached to the wheels of both axles, and the brake hydraulic system that controls the hydraulic pressure of each brake has a control system that releases the brake hydraulic pressure when the wheels are about to enter a lock state. An anti-lock control device is attached, and the anti-lock control device has a front wheel control section that individually controls the brakes of the front wheels, and a rear wheel control section that controls the brakes of the rear wheels. A four-wheel drive vehicle characterized in that a reference value for determining whether the vehicle is about to enter a lock state is set more gently than a front wheel control section.