JPS59742B2 - hydraulic brake device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic brake device that does not use mechanical friction force.

As conventional brake devices that utilize mechanical friction force, for example, brake devices that utilize mechanical friction force between a brake lining and a brake drum, or that utilize mechanical friction force between a brake pad and a brake disc are well known. However, these conventional brake devices have mechanical parts that wear out, have a short lifespan, are prone to failure, and also have problems with shock and noise during braking.Furthermore, as the device becomes larger, a brake booster is required. The problem was that the structure became complicated.

Therefore, the present invention solves these problems and extends the lifespan (
, fewer breakdowns, no shock or noise during braking,
A brake device that can obtain a large braking force with a small operating force, is compact and lightweight as a whole, has sufficient lubrication of rotating and sliding parts, and can withstand use even in the high-speed range of the braked shaft. The purpose is to provide

Therefore, the feature of the present invention is that the reciprocating body is controlled by controlling the flow rate of the liquid discharged by the reciprocating motion of the reciprocating body fitted in the cylindrical cylinder tube with a garden, thereby braking the movement of the reciprocating body. In a hydraulic brake device that brakes the rotation of a drive input shaft, the outer end of a cylinder tube arranged in a radial direction around the axis of the input shaft is swung within a plane orthogonal to the axis of the input shaft. The inner end of the reciprocating body, which is rotatably attached to the casing on the same circumference around the input shaft so as to be freely movable, and whose y-direction is oriented toward the center of the input shaft, is connected to the input shaft via a cam mechanism. The cam mechanism is interlocked with an eccentric cam fixed to the end of the input shaft, and its movement is restricted by a non-rotatable but radially movable mechanism. and a guide member to which the inner end of the reciprocating body is rotatably pivoted.

The present invention will be explained below based on illustrated embodiments.

In FIGS. 1 and 2, 1 is a hydraulic pump, for example a hydraulic pump.

2 is a pump casing of the hydraulic pump, and an input shaft 3
an inside cover 5 from which a spline end 4 protrudes;
It consists of an outside cover 7 which is fixed to the inside cover 5 in a closed manner from the right side of FIG. , 10, the input shaft 3 is rotatably supported on the inside cover 5 via the spline end 4, and the input shaft 3 is interlocked with the braked rotating shaft 11 at the spline end 4 so as to rotate integrally therewith.

This connection can be made freely by using a ← or a coupling, but it is also possible to make the braked rotating shaft 11 and the input shaft 3 integral to achieve compactness.

The braked rotating shaft 11 is a front axle, a rear axle, or the like of the vehicle.
Alternatively, the drive shaft thereof may be a rotating shaft inside the transmission case.The hydraulic brake device according to the present invention has many effects as described below, and is preferably used as a brake device for a vehicle. .

Note that a bearing case cover 12 is fitted with the input shaft 3 via a sealing material 13 to seal the inside of the casing 2, and is attached with bolts 14.

15 is a fixing member that fixes the pump casing 2;
In the illustrated example, a bolt hole 16 is provided in a part of the inside cover 5, and a bolt 17 is screwed into the bolt hole 16 to fix it. However, depending on the case, the outside cover 7 and the fixing member 15 may be fixed. , whereby the braked rotating shaft 11
Generates a reaction force when braking.

As is clear from FIG. 2, 18 is six cylinders arranged in the radial direction, and the guide member 1 to be described later.
9 are arranged in a narrow row at equal intervals around the circumference, and are pivotally connected to the pump casing 2 by cylinder pins 20 parallel to the input shaft 3, and are swingable around the pins 20.

As is clear from FIG. 2, the cylinder pin 20
are arranged in a meticulous row on the input shaft 3 at equal intervals around the circumference, and one end portion 20a has a disk-shaped outside cover 70.
The other end 20b is tightly fitted into the through hole 21 and has an annular ring 22.
The annular ring 22 is tightly fitted into the through hole 23 of the pump casing 2, and the annular ring 22 is also tightly fitted into the annular protrusion 24 of the inside cover 5, which is formed to protrude inside the pump casing 2.
b is pivotally supported by the inside cover 5 via an annular ring 22.

25V'i is an oil passage formed from the end 20a in alignment with the axis of the pin 20, and communicates with an oil passage 26 formed in the radial direction near the axis of the cylinder 18.

Thus, the cylinder 18V′i and the cylinder tube 28, which is a cylindrical body with a garden and is pivotally connected to the cylinder pin 20 through the bushing 2T, and the inner circumferential surface 29 of the cylinder tube 28 are slid in the axial direction. It is composed of a freely movable reciprocating body 30.

The illustrated example shows a case consisting of a reciprocating body 30Vi, a piston 32 having a piston ring 31, and a piston rod 33, but the piston 32 may have only a labyrinth groove or a plunger may be used instead of the piston. It is.

34 is a high pressure chamber, which is surrounded by the piston 32, the inner circumferential surface 29 of the cylinder tube 28, and the bottom 35 of the cylinder tube 28, and the high pressure chamber 34 includes:
An oil passage 36 formed in the bottom portion 35 and the bush 27
The oil passage 36 is divided into two parts with a predetermined interval apart in the axial direction.
and an annular oil passage 3 formed at a position corresponding to the oil passage 26.
It communicates with the oil passage 25 through two oil passages 36 and 37 of 7.

On the other hand, the end of the cylinder tube 28 opposite to the bottom 35 is open to the pump casing 2 .

Next, 38 is a cam mechanism that interlocks and connects the input shaft 3 and the reciprocating body 30, and the cam mechanism 38 has a function of converting the rotational motion of the input shaft 3 into the reciprocating motion of the cylinder 18. be.

Next, to explain this cam mechanism 38, 39 is an eccentric cam fixed to the inner end 41 of the input shaft 3 via a key 40 so as to rotate integrally with the input shaft 3. The cam 39 may be integrated with the cam 39, or may be fixed by other means such as a spline.

The outer circumferential surface 39a of the eccentric cam 39 is a perfect circle, and the inner ring of the bearing 42 is tightly fitted onto the outer circumferential surface 39a.

Reference numeral 19 denotes a guide member rotatably fitted to the outer circumferential surface 39a via the bearing 42, and the guide member 19 is eccentrically connected to the inner end 41 of the input shaft 3 as shown in the figure. A surrounding fitting part 44 surrounding the cam 39 etc., and the reciprocating body 3
and a mounting portion 43 to which an end portion 45 of the 0 is pivotably attached.

That is, in the illustrated example, the piston wand 330 guide member 19
The side end portion 45 is formed in a continuous manner as a short cylindrical body having an axis perpendicular to the entire axis of the piston rod 33 .

The fitting recess 47 of the guide member 19 corresponding to this is a cylindrical groove having an axis parallel to the axis of the guide member 19, as can be seen from both FIGS. The end portion 45 can be inserted from the right side to the left side in FIG.

Furthermore, the fitting recesses 47 having the cylindrical grooves are arranged at equal intervals on the circumference around the axis of the guide member 19.

In addition, even if a tensile force is applied to the reciprocating body 30, the end portion 45
is configured so that it cannot be pulled out from the fitting recess 47.

Reference numeral 48 denotes a non-rotatable but radially movable mechanism, the details of which are shown in FIG.
Convex strips 52 and 53 each having a rectangular cross section are provided in a protruding manner, and the protrusions 52 and 53 are arranged to be perpendicular to each other in a front view.

A concave groove 54 is provided on the end surface of the mounting portion 43 of the guide member 19, into which the protrusion 52 is slidably fitted, and
By similarly providing a concave groove 56 into which the convex groove 53 is slidably fitted at a corresponding position on the inner surface 55 of the outside cover 7, the guide member 19 cannot rotate with respect to the pump casing 2 and has a diameter. It is configured to be movable in the direction and its movement is restricted.

As described above, the cam mechanism 38 includes an eccentric cam 39, a guide member 19, a non-rotatable but radially movable mechanism 48, and the like.

As shown in FIGS. 1 to 3, the pump casing 2 is filled with a working liquid, and the tank 51
It is used for both purposes.

If hydraulic oil is used as the working fluid, this hydraulic pump 1 will be called a hydraulic pump, but inside the pump casing 2 are the rotating parts of the bearings 9 and 10, 42, and the end part 45. The sliding part between the fitting recess 47 and the protruding strip 5
There are many sliding parts and rotating parts such as the sliding parts between 2.53 and the grooves 54 and 56, the cylinder tube inner circumferential surface 29, the sliding parts between the cylinder pin 20 and the bushing 27, etc. Therefore, it is extremely preferable from the viewpoint of lubrication.

Next, 58 is a check valve, and through this check valve 58, the working liquid is sucked into each cylinder 18 from the pump casing 2 which also serves as the tank 57.

In the illustrated example, a prismatic valve body 59 with a hexagonal outer cross section is provided with a poppet and a spring (not shown) in the shape of a ball or cone, and the operating liquid is sucked through a suction port 60 .

The check valve 58 is fixed to the bottom 35 of the cylinder tube 28 with a screw or the like, communicates with the high pressure chamber 34 via the annular oil passage 37 and the oil passage 36, and is configured to be sucked into the cylinder 18. In addition, the valve body 59 has a thickness that does not interfere with the adjacent cylinder 18 or the inner surface of the casing 2 even if the cylinder 18 swings around the pin 20, and the mounting direction is also set accordingly.

Next, in FIGS. 1 and 3, 61 is a valve device, which is installed in the discharge side circuit 62 of the hydraulic pump 1 and controls the flow rate, pressure, etc. This is for applying a braking force to the braking rotation shaft 11.

In the example shown in FIG. 1, a valve block 64 housing check valves 63 is secured to the right side of the outside cover 7 with bolts or the like (not shown) in correspondence with the opening positions of the oil passages 25 of the individual cylinders 18. In addition, the oil passage 65 in the block 64 connects the annular oil passage 66 in the outside cover 7.
After the merging, the working liquid is sent to the valve device 61 by the discharge side circuit 62.

Of course, unlike the illustrated example, this merging may be performed by piping, or the individual valve blocks 64 may be integrated and an oil passage corresponding to the annular oil passage 66 may be formed therein.

Note that the number of cylinders 1B can be increased or decreased arbitrarily, so FIG. 2 shows a case of six cylinders, and FIG. 3 shows a case of three cylinders.

Thus, in FIG. 3, the valve device 61 includes an IJ valve 67 for controlling pressure and a switching valve 68 for controlling direction.

That is, when the pressure of the discharge side circuit 62 rises above a certain level, the relief valve 67 shuts down and the oil flows back into the pump casing 2 that also serves as the tank 57 through the return oil path 69.

Note that an acid screw hole 70 is provided in a part of the inside cover 5 forming the pump casing 2 in FIG.
The joint is screwed into this screw hole 70, and the return oil path 6
9 is installed.

Further, the switching valve 68 is exemplified as a two-position manual switching valve that connects the discharge side circuit 62 and the return oil passage 69.

Furthermore, the spool has a shape that allows the flow of liquid to be gently restricted during switching between the two positions of disconnection and connection.

In the normal state, as shown in FIG. 3, the liquid that has been brought into contact by the spring 71 and has flowed through the discharge side circuit 62 returns to the tank 57 through the oil passage 69, and therefore flows into the high pressure chamber 34 of the cylinder 18. No pressure is generated, the input shaft 3 rotates freely with almost no resistance, and the interlockingly connected braked rotary shaft 11 is in a freely rotating state in which the brake does not work.

Next, to reduce the brake force, push the spool upward in the figure with the manual lever 72. The spool gradually narrows the oil passage inside the valve 68, increasing the passage resistance and increasing the pressure on the discharge side circuit 62. The pressure in the high pressure chamber 34 in the cylinder 18 increases, and the pressure in the high pressure chamber 34 in the cylinder 18 increases.
A braking force is applied to the input shaft 3 and, therefore, to the braked rotating shaft 11 via the above-described structure of the cam mechanism 38.

If this spool switching is performed suddenly, the discharge side circuit 62
When the pressure inside rises rapidly and exceeds a predetermined pressure by the relief valve 67, it is relieved and damage to the components of the hydraulic pump 1, the braked rotating shaft 11, etc. is prevented.

And in the cutting state where the spool is pushed completely upwards,
While maintaining a predetermined pressure in the discharge side circuit 62 by the relief valve 67, the oil flows back to the tank 57 from the return oil path 69.

Next, FIG. 4 shows a case where a variable flow rate adjustment valve 73 that continuously controls the flow rate is installed as the valve device 61, and when the hydraulic brake device of the present invention is used in a vehicle, etc. If the foot pedal 74 is depressed in the direction of the arrow so that the flow rate can be adjusted easily and quickly, the valve 73 is gradually narrowed and the pressure inside the discharge side circuit 62 increases.
A braking force is applied to the input shaft 3 by the same action as described above.

It should be noted that the foot pedal 74 and the valve 73 are interlocked and connected as shown by the imaginary line in the figure, but specifically, they are interlocked and connected by a rond, a control wire, or the like.

In addition, the relief valve 67 is connected to the hydraulic pump 1 as described above.
In order to prevent damage to the components, etc., the valve device 61 is interposed so that the working fluid returns to the tank 57 from the return oil path 69.

In addition, this foot pedal 74 is connected to the switching valve 68 shown in FIG.
Alternatively, the manual lever 72 may be used as the variable flow rate adjustment valve 73.

Furthermore, it is also possible to control these valves 68, 73 by other signal transmission mechanisms such as solenoids or air cylinders.

As described above, since the hydraulic brake device of the present invention controls the operating fluid by the valve device 61, there is no shock or noise during braking, and it is suitable for various vehicles such as automobiles, construction vehicles, and agricultural vehicles. If used, it becomes an extremely excellent braking device, and therefore, it is preferable to select the front axle or rear axle of the vehicle as the rotary shaft 11 to be braked, or it is also preferable to select the drive shaft of the vehicle.

Further, although not shown, it is preferable to install a dustproof filter in the suction circuit to the cylinder 18, and it can be attached to the suction port 60, for example.

As described above in detail, the hydraulic brake device according to the present invention includes a valve device 61 interposed in the discharge side circuit 62 of the hydraulic pump 1 whose input shaft 3 is interlocked with the rotary shaft 11 to be braked. In addition to controlling the flow rate, pressure, etc., an operating liquid is sealed in the pump casing 2 of the hydraulic pump 1 to form a tank 57.
A plurality of cylinders 18 having reciprocating bodies 30 which are also used as the tank 57 and driven by the input shaft 3 are connected to the tank 57
Arranged in the radial direction inside the dual-purpose pump casing 2,
Since the system is characterized in that the working liquid is sucked into the cylinder 18 from the tank 57, there is no shock or noise during braking, and the pressure on the discharge side of the hydraulic pump 1 is controlled by the valve device 61. Since only the flow rate etc. are controlled, a sufficiently large braking force can be obtained even with a small operating force.

Furthermore, since the working fluid is sealed in the pump casing 2 and also serves as the tank 57, the rotating and sliding parts are sufficiently lubricated, resulting in less power loss when not braking, and less wear and tear. In addition, the whole body is compact and lightweight, and the length of the suction oil path to the cylinder 18 is shortened, so the suction resistance is significantly reduced and the working liquid can be easily sucked. This makes it possible to fully use the braked rotating shaft 11 even in the high-speed range.

Furthermore, if a separate suction port 60 is provided for each cylinder 18, the length of the suction oil path can be further shortened, allowing use in a higher speed range.

Furthermore, if hydraulic oil is used as the working fluid, the hydraulic pump 1 becomes a hydraulic pump, which improves the lubricity of many sliding and rotating parts inside the pump casing 2 and extends its life, which is preferable. be.

According to the present invention, the cylinder tube is pivotably mounted, and the reciprocating body fitted into the cylinder tube is operatively connected to the cam via the guide member that cannot rotate and whose movement is restricted by a radially movable mechanism. As a result, the cylinder tube and the reciprocating body can slide smoothly, and since the cam and the reciprocating body do not come into direct contact, there is no wear.Furthermore, since the cam and the reciprocating body are forced to move, they have good followability, and in the high-speed rotation range. No chattering occurs.

In addition, there is little rocking at the connecting portion between the guide member and the reciprocating body, and compared to a crank type, there is less vibration and less noise, so it has great practical effects.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional side view of a hydraulic brake device showing an embodiment of the present invention, Fig. 2 is a front view of the same partly in section, Fig. 3 is an explanatory circuit diagram of the device, and Fig. 4 is a An explanatory circuit diagram showing another embodiment, FIG. 5 is a front view of a non-rotatable but radially movable mechanism. 1... Hydraulic pump, 2... Pump casing, 3...
...Input shaft, 11... Braked rotating shaft, 18... Cylinder, 30... Reciprocating body, 57... Tank, 60
...Suction port, 61...Valve device, 62...Discharge side circuit.

Claims (1)

[Claims] 1. A liquid that brakes the rotation of the input shaft for driving the reciprocating body by controlling the flow rate of the liquid discharged by the reciprocating motion of the reciprocating body fitted in the cylindrical cylinder tube with a garden and braking the movement of the reciprocating body. In a pressure brake device, the outer end of a cylinder tube arranged in a radial direction around the axis of the input shaft is arranged around the input shaft so that it can swing freely within a plane perpendicular to the axis of the input shaft. The inner end of a reciprocating body is rotatably pivoted to the casing on the same circumference as the input shaft, and is oriented substantially toward the center of the input shaft. An eccentric cam with a circular outer shape is fixedly attached to the shaft end and has a center eccentric from the axis of the input shaft, and the reciprocating body is fitted onto the cam via a bearing and is attached to the outer periphery of the eccentric cam. It has a guide member whose inner end is rotatably pivoted, and a disc body interposed between the end face of the guide member and the opposing face on the casing side, and the diameter of the disc body is on the diameter of one end face of the disc body. is provided with grooves or protrusions, and grooves or protrusions are provided on the diameter of the other end surface in a direction perpendicular to the four grooves or protrusions, and the groove is slidable in these grooves or protrusions. Convex grooves or concave grooves that fit into the guide member are provided on the diameter of the end face of the guide member and on the opposing surface on the casing side, and by fitting each concave groove and the convex groove, the guide member is moved against the casing. A hydraulic brake device characterized in that its movement is restricted so that it cannot rotate and can move freely in the radial direction of a rotating shaft.