JPS58500988A - A master cylinder having a main spring and pressure area for applying the brake and an auxiliary spring and differential area for releasing the brake. - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] The main spring and pressure area for applying the brake and for releasing the brake. Mask cylinder with auxiliary spring and differential area The present invention relates to a fluid-operated hydraulic brake, and more particularly to a main body of a brake dam. Auxiliary springs and differentials for releasing springs and pressure areas and brakes 0 conventionally used power for a mask cylinder assembly having a dynamic area inside. The brake booster is a friction brake similar to the brake pedal operated by the automatic rotor. The brake acts hydraulically on the return spring so that the brake is only activated before the brake is released. At that point hydraulic pressure is released by the power source and the spring immediately applies the brakes. Return the booster and thrower to the non-active position. Therefore, the actual brake operation Use the full pressure of the power source only for the purpose of use.

However, the need for more complete utilization of power source pressure is desired, and the present invention addresses such a need. Satisfy the eel-ob-use. A certain type of brake that is different from the brake mentioned in Komata. One such need, already known in applications, is to boost the power source pressure. a retraction chamber or other accumulator as an emergency power brake retention means for additionally utilized to maintain the motor at full pressure. More notably, the power source application up to the full pressure of the power source to apply the brakes when desired, or when desired. Application of the full pressure of the power source to release the brake, from either the second and the second The sixth important point is that it is possible to find important uses. One implementation according to the invention Examples include a differential piston plunger within the master cylinder and also incorporate the principles of the present invention. According to Satisfied with Nja.

As will be explained in more detail below, the plunger provides a main pressure cutoff within the cylinder, which - main pressure The force is applied when the plunger performs a braking action assisted by the main spring. , and the plunger connects the auxiliary chisel-worth cylinder and the auxiliary shaft to release the brake. A differential pressure area is provided to receive the force of the retraction chamber due to the pulling action. more special Separately, for the stepped plunger and its differential pressure area, the auxiliary spring The power element operated by the spring is pressed inside the chamber, and the power element is The element does not necessarily have to be stepped, but it still consists of a piston with a stepped structure. .

However, the main advantage of having a main pressure truncated and differential pressure region is that the main region is the source of the fluid supply. A brake that is accurate enough to be able to shift pressure in response to the full pressure of The differential pressure region W is capable of pressure movement in response to the total pressure of the same isolated source. The brake release action is accurate. These two interact 5JliJjjk’, the system shall be reproduced in the paragraph briefly described below. It is powered in a manner that it is believed that the term drive is immediately applicable.

The patents that form the background of this invention include U.S. Patent No. 2532801゜3 Japanese Patent Publication No. 58-5 00988(5) 2991758, 3242825.　5462986゜35227/)0. reactor 896706. 4253306. and No. 4256017. Also, additional U.S. Patent No. 2992630. 35761.52 and 3911 There is No. 795.

One object of the invention is to release the brake with full drive power while The purpose of this project is to propose a double-drive system that is huge.

Another object of the invention is that the hydraulically braking drive force is The object of the invention is to provide a system of hydraulic action.

Additional objects of the present invention are completely different in character but smoothly related to each other. A multimodal system with power braking that occurs in two modes or stages. It is about providing.

A related object of the invention is to provide a dual aspect system in emergency operation. be.

A further related object of the invention is to simultaneously control other vehicle parts, especially Dual aspects for braking applications with and without automatic neutralization of the transmission The goal is to provide a system for

Another object of the present invention is to prevent valve linkage damage and mechanical The object of the present invention is to provide an additional system as a safety measure in connection with mechanical damage.

One additional object of the invention is that the axle included in the twin braking system Separate hydraulic braking by individual mask cylinders contained in the stem. An object of the present invention is to provide a system including a double-acting cylinder that can be rotated.

Yet another object of the present invention is to provide a connosect design for connecting the mask cylinder and foot. To provide a device in which a booster valve and a booster are integrated into one device. .

Another object of the invention is that the pump is actuated immediately in response to the brake setting, but the gear To provide a brake system driven by a pump that does not suck as much oil as possible. It's there.

Another object of the invention is to provide a power brake function in addition to normal service brakes. In addition, the normal service brake is the sixth brake, which is the normal parking brake. emergency so that a small design can be made when the Its purpose is to function as an emergency brake, which is sometimes used for stopping.

Another object of the invention is that in the case of power losses, it can be used in a number of applications, e.g. the application is formed conjointly with the emergency power or is at least assisted by the emergency power, and Then countless applications were developed without the aid of a fourth rater and with other systems. O is made to resemble a straight through the braking action of the stem. The objective is to provide a motor-operated power brake.

Other features, objects and advantages of the invention are described in the appendix, which describes one preferred embodiment of the invention. It will become apparent when the invention is better understood with reference to the following description in conjunction with the drawings. It will be.

Figure 1 shows a specific example of the present invention in a normal vehicle in full drive brake release mode. longitudinal cross-section of the master cylinder assembly; Figure 2 shows the same parts of the brake master cylinder in released emergency assistance mode. A line diagram showing, FIG. 6 is a diagram of the same part in its released, non-assisted mode of action; Figure 4 is a diagram of the same component in the non-assist mode when activated, Figure 5 is the power control. The same is in a state corresponding to a slightly set brake due to the spring pressure under the A diagram similar to Figure 1 showing the parts, Figure 6 shows the brake in the position set at full spring pressure under the power control. A diagram similar to the corresponding FIG. 5, FIG. The figure shows the relationship between pressure and brake torque over a deep brake stroke. Graph, Figure 9 is a hand renomy aid that provides an additional means to the brake actuation system. 2 shows a detail view of FIG. 1 with a modified mode of operation; FIG.

In order to include all the different views in Figure 1, the master brake cylinder power assembly A degree of freedom in drafting is incorporated to the extent that the assembly 10 can be achieved. Figure 1 is a front view Approximately 6 Seen in several drawings of the front view and side view (in the front view, elevations are indicated by 12α and 12h). It focuses on the rectangular box-shaped housing 12 that is used for power brake assembly. In front view, this housing for the auxiliary differential piston 14 and the differential valve 1 It is broken at 12α to expose 6, and these pistons and valves have a common It has a vertical stroke axis 18. Complementarily, the housing 12 has 12h on the side. Shown in cutaway, this allows the horizontal stroke axis to be aligned within the dual cylinder extension 66. A differential piston syringe 24 with 26 is exposed at the rear.

Furthermore, in the brake assembly of FIG. 1, the brake 22 requires power drive. A vehicle 20 with im-tires is shown by a solid line 28 and a dotted line 28h on the right side of FIG. It has a power shift transmission shown in . Also, O of vehicle 20 is for Rator. The brake pedal assembly is shown in dotted line 60α and in solid line at the bottom of FIG. 30h.

As an additional assumption, something quite additional is built into the workings of the actual system in this N. Hydraulic or mechanical damage such as power loss, linkage damage or control valve damage In an emergency situation that may result from mechanical destruction, the various routes intentionally taken Due to the control, O is now protecting Leta. Front and rear axle 3 2 and 64 have their own master in extension 66 for appropriate brake 22. Controlled individually by cylinders 66α and 36h, the brake is activated. In use, they are additive to each other at the front and rear.

Special notes on Figure 1 A differential piston plug is provided in the cylinder of the double cylinder extension part 66 so as to be movable in stages. Since the plungers are identical to each other, only the differential piston plunger 24 is shown. There is.

The differential piston plunger has a hydraulic brake guide separated by a differential valve designated 12α. controlled via tubes 38a, 3El, the plunger is connected to the vehicle brake 22 control.

The plunger proper 40 of the actuating piston plunger 24 is a block. Shown in fully retracted position for rake release and with relief 42 at the end It has a passage 44 for a directional ball check valve. Pole check passage 44 Hatsune It communicates with an oil tank (not shown) through an opening 46, which allows the plunger projector to When the par 40 is retracted to the position shown, the proper draws a vacuum in the cylinder 66a. prevent it from entering. At the end of its backward stroke, the plunger relief 42 Due to the permanently open restriction opening 48 between the oil tank and the oil tank, there is no misalignment with the oil tank. The pressure between the cylinder 36a and the cylinder 36a is equalized.

The differential piston plunger 24 has a stepped portion 50 and a large diameter piston that can support the seal 54. The stone portion 52 has a small diameter plunger proper 4 by which the seal 56 can be supported. Separated from 0.

The resulting pressure differential U] area B is the area B of the cylinder forming the differential area pressure chamber 60. It moves within the cylindrical enlarged portion of the cylinder 66α. The main area channel 2 has a differential pin inside it. The main pressure excitation valve 64 of the stone plunger 24 forms a moving volume and 64 has a hollow interior 66. The hollow interior 66 has a main spring 68 and a Then there is a spring chamber around it that accommodates a weak spring 70 that assists the main spring. Configure.

The differential chamber 60 receives a fluid such as oil from the regulated release pressure conduit Pi. main area chamber 6-2 receives flow from regulated working pressure outlet conduit P2. Pressurized by the body. A drain D connected between adjacent seals 56 is connected to the chamber 6 0 fluid and the brake fluid in cylinder 36a do not mix with each other. , and does not allow any leakage through the seal to accumulate within the extension 66.

The differential pressure detection switch 72 connected across the hydraulic brake conduits 38a and 3El is , is included in a brake failure indicator circuit having a lamp 74 on the vehicle instrument panel; The pressure in one of the two conduits, which should be the same, has decreased relative to the other. Lights up when. At this time, the lamp indicates, in a known manner, that the brakes are at idle. It will continue to light up even after.

In the vehicle 20, the front wheels 76 are mounted on the front vehicle so that the front wheels 76 can be steered relative to the rear wheels 78. Although a steerable wheel structure can be provided for the vehicle, the vehicle shown is articulated. Each section has fixed axles 62 and 6 at the front and rear. 4. The front vehicle #62 brakes due to the brake hydraulic pressure from the conduit 38a. However, the rear axle 64 is connected to a separate mask cylinder 56h. The brakes are applied by hydraulic pressure from the rake conduit 38h.

The brake action is controlled by the pedal action assembly filter Oa, which will be described later. Ru.

The power brake assembly, shown as 121Z, and the transmission, shown as dashed line 2Bb. Each section uses fluid pressure to operate the power shift transmission. To operate the power brake rather than the scale, the receiver is taken and sent out.

More specifically, the transmission 28h supplies a pump source 80 of pressurized fluid to the illustrated A more convenient rear end point on a suitable transmission than a convenient rear end point for display. Drive F-1 with good actual points. Pump source 80 supplies the regulated pressure to the header. Exit conduit 82 feeds a beader 84. Housing 12 α transfers fluid at a regulated conduit pressure P to a second countersink supplied by header 84. 86, and the counterbore core is located at the vortex at the sorake release position shown in the figure. Closed by.

The first counterbore core 88 is a check valve and a restriction means for controlling fluid flow at pressure P. through the assembly 9D of the receiver 10 and a release pressure conduit arranged so that the fluid is supplied directly to the differential chamber 6o. Send through P1. This flow then occurs without reducing the flow tube pressure P. What If so, the seated ball regulating valve 92 in the piston shown is then calibrated. This is because the adjustment spring 94 holds the differential valve firmly against the seating surface within the differential valve. When activated, valve 92 regulates the pressure in conduit PJ to a reduced value.

Retraction chamber 96 connects check valve and restriction assembly 98 from header 84. The normal conduit pressure P is maintained through the differential valve 16 in the fully retracted position as shown in the figure. Have a single exit that is only valid at certain times. Retraction chamber pressure is different with constant bias force It acts on the differential area V100 of the valve train 16.

More specifically, the single outlet for the retraction chamber 96 is connected to the valve in the differential region 100. is formed by a starting face relief and includes a chamber 96 and a first counterbore core 88; It is provided with several short longitudinal valve slots 102 formed in a direct manner between the It is growing. In this way, the retraction chamber 96 also has a regulated pressure relief outlet. It is directly connected to the differential chamber 6o by a pipe P1. Therefore, the total conduit pressure P is the valve 16 positive. Therefore, as far as it can be obtained, the differential chamber 6o has two separate loops 102, 90. 84 (through the manifold), the differential piston plunger 2 4 is held in the brake release position shown.

The main region 104 of the auxiliary actuation piston 14 faces into the passage of the differential region 100 of the valve 16. and one of the two is moved across chamber 96 into engagement with the other. I can move. Piston 14 slides with its internal bore over the small diameter portion of valve 16 . A conventional circular liquid balance groove 105 is provided at the sliding head.

The auxiliary histone 14 is nominally a differential piston. And deflation The mechanical area 1o6 is a heavy area located within the spring chamber of the cylinder 12α. A spring seat for the load auxiliary brake spring 108 is provided. vinegar The pull 108 is attached to the end cover 110 of the power brake equipment housing. Add a reaction. This reaction is mechanically parallel to spring 108. It is supplemented by an attached second light load auxiliary spring 112. No. The spring 112 of No. 2 is connected to the piston 14 which slidably receives the stepped pulp 16. located concentrically between inner stop sleeve 114 and spring 108 for be positioned.

It has lever ends 118, 120 at its right and left ends as shown in FIG. The crosspiece is connected at its center to a pivot 122. Therefore, for leverage Therefore, when tension is applied, the differential valve 16 is activated. . The crosspiece 116 is, for example, a pedal connected to a brake pedal 126 of the pedal device 30A. It is actuated by pulling down the left lever end 118 through the barrel connection means. Ru.

Figure 1 shows the full power state of the device according to the invention, i.e. This figure shows a state in which the rake is released.

Lifted emergency assistance -m-Figure 2 In this figure as well, the differential piston plunger 24 is completely inserted as described above. The brakes have been completely released. However, the fluid pump loses power. The auxiliary spring actuated by the auxiliary piston 14 is shown in FIG. For example, for a full stroke such as ing. Therefore, the volume of the retractor chamber 96 is reduced, thereby reducing the volume of the retractor chamber 96. Fully fill the french chamber 60 and release the plunger 24. Ru. , under fluid loss of the pump source, automatic displacement of the auxiliary piston 14 Decreasing motion is how much braking is required to overcome the motion of the system. depending on the size of the emergency power assisted brake release. . To give a specific example, for example, if the brake is released from a full brake state, +7) If the emergency fluid in the lactator chamber 96 The amount required to release the rake is ℃・ru.

Released without aid -m-Figure 6 After the emergency pressurization fluid is evacuated from the retractor chamber 96, the plastic The trigger 24 may be operated by the driver to the fully released state as shown in the drawings any number of times. can be made. However, unlike the case in Fig. 2, the auxiliary piston in Fig. 6 Ton 14 presses the spring 108 again with the brake pedal and releases it. After performing a simple foot operation, the stroke will be at approximately % of the full stroke. . However, the limit of the stroke still maintains a completely released state of slippage. .

In such an unaided state, the auxiliary piston 14 is at full throttle for reasons explained later. Start moving to release until approximately % of the stroke is reached.

Adaptation/No aid -m-Figure 4 While applying the brakes, i.e. in the drawing part 24, the brakes are applied without power. While applying, the operator will later refill the chamber 96 solely by foot force. It is necessary to move the differential valve 16 forward. At the same time, the data engages the auxiliary piston 14 in the french zone 100 and carries it through the full stroke. Return to approximately % position. The reaction force of the auxiliary spring 108 for heavy loads is applied to the driver's foot. Force alone determines how far the piston 14 will retract. On average, with the power of your legs The static force required to push the pedal down is approximately 125 pounds (56kl?) It is.

Thereafter, the driver was added to pulp 16 as explained with reference to FIG. Release pressure on your feet. Thereby, the piston 1 actuated by the auxiliary spring 4 reduces the volume of the chamber 96 for complete release of the brake.

The above-mentioned emergency operations can be carried out using the emergency reserve power and It is a two-way operation without using a reserve. , for example, it is possible to repeatedly apply the brakes 30 times or more. can.

Powered operations are somewhat interconnected, as explained in the next section. This operation also It is a two-way operation, so that the brakes are applied in stages, but in two separate It is designed to include successive stages.

Power-controlled brake set slightly by spring pressure -m- FIG. 5 The brake is tapped one or more times on the barrel 126 as shown in FIG. The differential piston plunger 24 is placed in its predetermined initial braking position. need to be moved. Such initial movement of the pedal causes the tension coupling means 124 to , swings the end 118 of the crosspiece 116 about the end 120. This end 12 0 rests on the end cover 110, and the crosspiece 110 acts as a lever against the cover. Encourage them to use it. The full line pressure P causes the retractor chamber 96 to The volume is now fully enlarged and the closed slot 102 is therefore , the differential piston 14 is kept stationary, but the full stroke, i.e. That is, as explained in the fully retracted position, it is ready for that complete emergency position. held in state.

Yet another configuration of the differential valve 16 includes a pivot connected to the crosspiece 116. 122 becomes of significance when such a predetermined movement of valve 16 occurs. problem and This part is a hollow, enlarged diameter valve tip.

Initially, the valve 16 is disposed as a core at one end of the valve hole in the device housing. Begin exercising by putting in the slug 128 and letting the puppy out. Valve 16 side A drain port 162 through the in-plane hollow wall is connected to a calibrated adjustment spring 94. Remove the cover from the portion of the slug shoulder 1 and 4 that provides a stop for the slug shoulder 1 and 4. , 1- The bolt 132 therefore passes through the spring chamber 168 into the valve. an empty interior 1 filter 6, generally designated by the number 140, and a fill oil pipe reservoir; Open to the 1.゛lene pressure through a connecting means extending upwardly and connecting to the drain D. are doing. The spill Ome line leading to drain D is also located below piston 14. Spring channel on the other side: also communicates with the long vertical oil distribution pipe 141 that leads to V. There is.

Second, the other end of adjustment spring 94 is restricted to flow into first hole core 88 . The ball adjustment valve 92 is operated to adjust the back pressure of the fluid. This means that the valve 92 , the valve system of the bore core 88 through the axial and radial passages 142 of the valve 16. This is because it communicates with the route. In addition, the input and output rollers with adjusted release pressure In P1 similarly reduces the pressure P1 in the differential chamber 60. child As a result, the main spring 68 and the weighted spring 70 move the plunger 24 into the cylinder. It is possible to start moving in the direction of applying the brake within the cylinder 6O.

6 When the barrel 126 is released, all components are removed as described with reference to FIG. The power will return to the brake release position.

Closed 8 system stroke --- Figure 5 Figure 5 shows the emergency no-assistance state There is no illustration. However, this condition is similar to when fluid pressure is lost. In an emergency, use the force of your foot to push the brakes beyond the position shown to apply full brakes. This corresponds to pushing down the lubricant 16, which can be easily imagined from Figure 5. It is something.

In this condition, the auxiliary differential piston 14 is in the position shown. do not have. The piston 14 is located above the position shown in the cylinder and Valve 160 is positioned in contact with abutting differential region 100 . Rifi Check valve 1 connected to reserve oil maintained in oil distribution pipe reservoir chisel 140 4. Immediately leave the retractor chamber 96 and refill the retractor chamber 96 with fluid. Fill. That amount is created when the suction surface 104 of the piston 14 is pulled down. Equal to the volume L°C.

At the same time, the ball regulating valve 92 moves away from its valve seat, so exactly the same amount of oil is released. A predetermined amount of reserve fluid is always maintained from the differential chamber 60 whose volume has been reduced. The refill oil pipe is moved to the right toward the inside of the reservoir 140.In fact, Most of the oil (though not all of it) in the chamber 60 whose volume has been reduced is directly into chamber 96 through check valve 146 when it is manually inflated. Move tangentially.

Counter heart stroke --- Figure i3 Released unaided position of piston 14 The spring forced movement (see Figure 6) is transferred into the retractor chamber 96. The valve-controlled charge path 102 (not shown) maintains the flow rate that has been ) is used to re-move through. As a result, the plastic inside the chamber 60 The movement of the chamber 24 in the direction of brake release, which reduces the chamber, is caused under pressure. It is done.

The cycle then repeats. That is, opening chamber 96 again Press the differential piston 14 again with the force of your foot, and 6 into its brake application position. Pushed from the differential chamber 60 The drained oil passes through the valve control release path 92 (not shown) to the sixth valve control release path 92 (not shown). By the downward movement of the differential histometer 14 as shown in the figure. It flows into the created equivalent amount of Risano ε.

This new fill oil piping reservoir circuit design allows the reservoir 140 to There is no oil in the flow to the oil distribution pipe 141 shown in the figure or to the train 9 D. There is no content loss. Therefore, the emergency auxiliary differential piston 14 can charge the chamber 96 located above it, and the chamber 96 located below it. Spring channel no. 4 reservoir circuit 140 and oil distribution 18 located on the side It can be repeatedly refilled through channel 141. Reservoir circuit 140 and Oil line 141 normally fills the system with oil and therefore Prevents the formation of air bubbles and cavitation due to repeated brake operations.

Power control, spring full pressure set The force of the driver's foot causes the coupling means 124 to be placed beyond the position shown in FIG. When moved, the differential valve 16 moves further downwards as shown in FIG. be lowered to the indicated position. This results in a recessed valve seat and an adjustable valve Open a gap between 92 and 92. This idea is based on an inflow and outflow rotor with regulated release pressure. Line P1 reduces the pressure in the differential chamber 60 to the drain pressure. Therefore, the springs 68 and 70 are connected to the plunger 24. deflects to the brake position with full spring pressure without obstruction or assistance. Chew.

The graph reached by this pedal stroke, as illustrated in FIG. The corresponding points on 5 are the point 144 where the adjusted pressure P1 is zero, and the point 144 where the regulated pressure P1 is zero, and This is a point 146 where the torque P1 becomes a considerably large value. The ball control valve 92 The reason why it separates from the lube seat is that the spring 94 for the ball control valve 92 In the state shown in Fig. 6, it is fully extended, and the input/lower output line P 1 is in free communication with drain D at position 162. Already hinted at that As shown above, the short slot 102 is in the out position unless it is in a completely released state. , the retractor chamberer 96 is completely separated from the input/output line P1. separated.

A second set of elongated short slots 148 of variable depth on the valve 16 It ends just before the hole core 86 of No. 2. Therefore, the pressure P is the input/lower output line P 2.It is designed to prevent it from entering inside. In reality, until this point , the sixth hole core 150 providing line P2 has a variable depth slot 148. The main tomb chamber 62 is connected to the spring chamber 168 and the drain D through the It was continuously connected to the drain line 140. Therefore, the previous During this time, the unpressurized main pressure movable part provides assistance to the operation of the plunger 24. It neither helps nor hinders.

However, when the valve 16 is pulled down further, the variable depth slot 148 , the third hole 86 was gradually brought to the spring chamber and then to the line pressure P. becomes connected to. Therefore, the input/lower output line P2 with adjusted pressurizing force is , through the slot 148 and the sixth hole core 150, the main pressure movable portion 64 is gradually Pressure is applied. At the same time, the differential chamber 60 has an adjusted release pressure. The low pressure is always maintained at pyrene pressure by the low output line P1. held.

Full Power Brake Braking - 11 In the condition shown in Figures 7 and 8. In this case, the differential piston 14 has a full stroke as described with reference to FIG. It is located at the same location as the market. Chamber 96 receiving full line pressure P is expanding to its maximum volume. However, please be especially careful here What should happen is that the valve 16 is lowered to its maximum stroke position and the full line pressure P □ is applied to the main pressure movable part 64. Theoretically, The adjusted pressure P2 of the input/output line P2 whose pressurizing force is adjusted is the line pressure. by reaching the line 152 on the flat graph in Figure 8 that corresponds to P. The effect appears. On the other hand, the brake torque T2 is the full brake torque. line 154 on the curved graph.

The valve mentioned above is somewhat exaggerated compared to the real thing. 1 case and Although this will be explained using specific numbers, this is also an example for complete understanding. Therefore, it is not intended to limit the present application. Pressure P is 300psi (21kg/crt r”), and the adjusted pressure P2 is 200 psi (14kl?/cIrL2). Ru. Point 156 in FIG. 8 gives the corresponding brake torque T2, and point 15 on the curve 8 is sufficient to provide full braking force and complete stop under any conditions. Ru.

Power operation has the following characteristics. That is, the initial stage of the full valve stroke from the fairly high pressure P at the stroke to the pressure D at the mid-stroke point 144. The outlet pressure P1 decreases at At the end of the stroke, at point 152 (see Figure 8), the pressure rises to a fairly high pressure P. A second outlet pressure P2 is provided.

In FIG. 7, when the driver releases the valve 16 from the position shown, the valve 16 is released. The released spring returns the brake system to the fully released state as shown in Figure 1. It works like this.

As is clear from the difference in the drawings of the valve 160, the operating timing of the master cylinder 66α is Chambers 60 and 62 are for non-assisted braking or emergency braking operated by the driver. Whenever the drain pressure is to be unobstructed, valve 16 It is maintained in

Brake - neutral, pedal load - m - Fig. 1 Brake pitcher 124 is pressed down When the torque converter 1 installed in the power conversion transmission 2Bh 60 allows the transmission to slip and its input side is stopped by a brake. make it possible to do so. Brake - pedal device 3 known as neutral hard pedal 162 Other members at 0h do not brake with the transmission 28h even if the brake 22 is activated. flexibility is provided to avoid conflicts with key 22.

For this purpose, the header 84 has an aperture 22 Line pressure is routed through the inlet 164 into the equipment housing below the end cover 110. It has a plunger 168 positioned at and protruding outward from the plunger 168. Supplied to the normally closed transmission control valve 166. fluid pressure The force forces the protruding plunger 168 outwardly to the dashed position 168a in the figure. -Valve 166 applies line pressure P to power via line 170. Connected to the neutral knob N in the controller of the shift transmission 28b. Ru.

Thus, the coupling means 172 is operated between the pedal 162 and the end 120 of the crosspiece. , the depressed pedal 162 swings the end 120 to the position 120 indicated by the dashed line. Set it to the α position. At this time, the end portion 118 of the crossbar becomes the fulcrum of the lever.

Applying the brakes by pulling valve 16 outward will cause the transmission to The protruding pusher 168 of the action control valve 166 is located at the extended dashed line position 16. I will get an 8a. This will automatically start the transmission 28A. A pressure signal is generated to set it to neutral. Therefore, the transmission drive The torque converter is used to ensure proper braking without interfering with braking. No special reliability is required for the data processor 160.

Second, the offset key neutral pedal can be operated independently of the brake pedal 126. Because of this, the reserve operation Nyo 23 Special Table 1988-5009880 In the event of failure of the coupling means 124 or the brake pedal 126, the driver should Can perform nomic azo control. Two dal 126.162 is water The flat fixed axes are mutually oscillated so as to have a common axis 176. installed.

Brake/Throw Duplicate Function -m-Figure 1 If the link mechanism fails, the normally closed valve 174 Move the brake pedal to the opposite position 126α. So the driver By pushing the lever 126 to the overtravel position, under that condition the normally closed sol The key 4 valve 174 can be opened. Box 174 is the inlet-outlet pipe P1 and outlet connection It communicates directly with the riser pipe 141 to completely reduce the pressure in the differential pressure chamber 6o.

Therefore, overlapping functions are accepted inherent in the driver's natural behavior and the spring 68.7o allows braking to be applied in the event of brake linkage failure.

Handle duplication function -m-Figure 9 In the modification shown, the handle 176 is a manual aid for braking. give. Sealed back cover 178 is supported by assembly housing 12a. 9, and the pivot constriction 180 on the cover is rotated clockwise in FIG. The handle 176 is supported for rocking motion.

Pushable brake addition plunger 182 sealed at 184 on the back cover protrudes outward and the handle 4 176 and the differential valve 16 with which it abuts are engaged in a compressed state.

By rocking the handle down to the position indicated by dashed line 176a, Press the valve 16 and apply the brake as described for the single tree 116. causes a spring engagement. Spring 18 is released by releasing handle 176. 6 and release the brake.

This is because the valve 16 immediately returns to the position shown by the solid line. spring What the valve 186 provides to the valve 16 is a mechanical safety function (fail-5afe). It is.

The driver receives manual overlapping functions to set the brakes. I want to mention the above By making it easy for some redundant functions to be provided, This is made possible by the ring 68.

By carefully analyzing Fig. 8, we can see that the changing pressure P1 is automatically Now you have a dynamically regulated pressure, accurately predictable valve, and the best constant for the susol stroke to ensure smooth initial brake engagement. Gradually changes in linear speed. However, under the control of the changing pressure P2, it is completely blocked. Raking doesn't have to be very sensitive. Therefore, the pressure Increases and decreases are somewhat steep per unit stroke, allowing for precise spring adjustment Not subject to automatic adjustment by valve.

Careful consideration of the converter-driven pump 80 during normal operation 5 A detailed analysis shows that at low speeds, such as when the engine is idling at low speed, the oil output is only 2 to 6 gallons per minute, and can be controlled solely by the transmission. One thing became clear.

In this device, the brake is first applied to the output of the pump 80 from the transmission. Instead of separating the Therefore, it is shaded. Therefore, the second part by reason of diverting the oil There is no opportunity to interrupt the transmission operation even when engaged The braking reaction is instantaneous. The reason is that the release of oil from Ken 60 is actually This is because it is instantaneous.

During a so-called direct braking operation in the event of a power failure, valve 16 operates the valve 92. Each time the differential pressure chamber 60 is released by removing it from the seat, the direct braking may diverge. Recognize. Just as Masu 16 lets go of the brakes, the brakes will follow sooner or later. When the pedal is released, the reactor ￥96 uses the reverse IL cell 146 to adjust the total fluid to the differential pressure rate. 60 and do not return all fluid to riser reservoir 140 or use an auxiliary stream. A drain D connected to the spring chamber occupied by the pull 108 or Do not return all fluid to connections from the latter, such as riser 141.

At each point at which the valve 16 is returned from the protruding position, the reactor base 96 is exposed to residual positive pressure. It always remains in the state of ℃・ru. Therefore, the differential area of the differential valve 16 is is 26 dal Pressure movable safety that returns the retraction valve to its brake disengaged position when released fail -5afa) Acts as a braking area. In other words, the design of this differential valve is In addition to being a mechanical safety device 186, the auxiliary brake actuation spring 10 It is guaranteed from this unexpected feature given by 8/96 pressure It also serves as a fluid safety device. Even in the event of a fluid failure of the pump 80, Oil begins to flow out of the differential pressure lock 60 after a few minutes and the brakes are gradually turned off. but , engaged, or engaged brakes will force either brake pedal 126 or 162. (It is quickly released again by stepping on it to release it.

Principle for releasing the differential pressure and immediately applying the safety main spring to the brake instantaneous response given under (compared to), this book has a dual actuation device and a double for normal braking and emergency braking. The application function offers unique driving advantages and at the same time the components suggested for the vehicle. Compatible with small design parking brakes. This compatibility is Stop the vehicle using the brake pedal, then apply the small A-king brake and press the brake pedal. It will become clear when you release rakey-efk. Because the pedal device This is because release transmits sufficient braking load to the parking brake. Therefore The driver can immediately know whether the parking brake is held or not. can.

27 Special Publication Showa 58-5 (10988 (11) Gradual oil spill from the royal family dissipates in a few minutes The re-expanding main spring fluidically sets and brakes the safety R-dall device, and Specially enhanced parking brake action with independent braking action to maintain let

Variations within the spirit and scope of the invention will likewise be understood from the above description.

Engraving (no changes to the content) Procedural amendment (formality) April 1980/φ day Chief of the Suspension Agency: Mr. Kazuo Wakasugi 1.Display of the incident PCT/US 81100843 3. Person who makes corrections Relationship to the incident: Applicant address Name: International Harvester Company 4 Agent Address: 2-2-1-1 Otemachi, Chiyoda-ku, Tokyo Contents of amendment As per the attached document (there is no change in the contents of paragraph (3)): International Search Report

Claims (1)

[Claims] 1. A master cylinder assembly having a main chamber and a differential chamber in the cylinder. and a slidable differential piston syringe (24) having a brake release mechanism therein. has a silanger area (i0) sensitive to hydraulic reaction pressure acting in the direction; a main spring - (68) and by the pressure acting on the main IZV in the main chamber (62), the main being made mechanically and hydraulically movable with a force coupled in the direction of braking; Piston Ward! a piston plunger (64) having a differentially liquid-releasable pressure chamber (60) in the cylinder, in which the supplied liquid Body pressure is applied to the actuating section M, (58) of said movable differential piston plunger. A pressure chamber is applied in the brake release direction in the opposite direction to the combined force of the main spring and the main area pressure, and the liquid inside the pressure chamber is pressurized to release the brake in the release direction, and the main area pressure is applied in the brake release direction. Overcome the combined force of the spring and the remaining pressure in the main area. (156) to pressurize the fluid inside the main chamber 1, thereby Therefore, the combined force of the main spring and the main partition is in the direction of braking action. means (16) for producing a braking action at the master brake series; da aggregate. 2. A development of claim 1, which causes both pressurized fluid pressures to be released simultaneously (as indicated at 144), thereby providing only mechanical control from the motion produced by the main spring. An invention that made this possible. 6. In a master brake cylinder assembly that has a main chamber and a differential chamber in the cylinder. a slidable differential piston plunger in which the piston plunger is arranged in the direction of brake release; The plunger chamber is sensitive to the hydraulic reaction pressure acting on the plunger chamber, and the mechanical force is applied in the direction of braking by the pressure acting on the plunger chamber in the main chamber. a differential piston plunger having a main piston section which is hydraulically movable; body pressure is applied to the actuation section of the movable differential piston plunger, The combined force of the pulling main area pressure is applied in the opposite direction to the brake release direction. a pressure chamber configured to reduce the supply mechanism over the entire stroke of the valve; The output pressure (Pl) of The pressure is maintained up to the point where the pressure is initially low but reaches a substantial pressure level only when the full stroke is reached. a valve for providing a decoupled output pressure (P2); a first (indicated by P2 in FIG. 1) and a second flow means (indicated by Pl in FIG. 1); One is located between the liquid inside the main chamber 30 and the disconnected output pressure P2 of the aforementioned 1, and is connected to the main spring. the combined force of the differential chamber and the main separation pressure causes the brake to be applied in the brake application direction, and the other is between the differential chamber and the first output pressure P] and causes the brake to be applied in the release direction; A master brake cylinder assembly having: a flow means adapted to overcome the combined force of the main spring and the residual pressure in the main area. 4. In the aggregate according to claim 3, the means operated by the sweeper Therefore, under all circumstances the operator can move the valve up to at least the mid-stroke of the mechanism to ensure the discharge pressure, thereby reducing the actuation of the main spring and the pressure present in the main area and any coupling. An assembly in which only the force exerted by the brake is applied in the direction of braking. 5. In the assembly according to claim B, the box of front = e is arranged to take a position for brake release and liquid transfer, and further includes an auxiliary spring, a differential piston, and a cylinder in the assembly. and thereby limited to one side of the differential piston A retraction force in said piston causes the fluid force on said one side to be balanced by the latent force of an auxiliary spring acting on the opposite side of the differential piston, and includes a square in said mechanism; When the valve assumes the transition position, it forms a passageway and Therefore, the force of the auxiliary spring is 3] The fluid in the drawing chamber is forcibly transferred into the differential chamber by A passage type that allows the brake release movement to occur due to the operation of the differential piston Zolandia. An aggregate that has the means to create. 6. An arrangement according to claim 5, in which the valve is arranged to occupy a transition position which is only initially present prior to the initiation of the valve stroke. 7. In the assembly according to claim 5, said valve comprises a differential valve and during the valve stroke in said mechanism, the differential partition is forced through the recess; The movable piston faces the valve actuating area in the retraction chamber and thereby strokes the valve. an assemblage adapted to be engaged for a mechanically forced retraction stroke within said chamber during the arc. 8. A power brake cylinder assembly having a recess in the cylinder (12a). The differential piston (14) and the differential valve (16) in the cylinder one side can be slidably engaged with the other over a retraction stiffener in the A piston in the valve is arranged opposite one working area (100) of the valve, said differential piston having an auxiliary brake spring (108) on the opposite side of said piston so that said piston is forced by a retraction force. so that it can be moved until the pressure is applied to it and the pressure is balanced by the latent force of the auxiliary spring. 2. The front=p differential valve has an outwardly projecting end suitable for causing a braking stroke of the valve to be effected by an operator, thereby The differential section of the valve is drivingly engaged with the differential piston and mechanically applies a force to the differential piston to cause it to move until the force is equally balanced by the latent force of the auxiliary spring. A brake cylinder assembly characterized by. 9 In the assembly according to claim 8, a vehicle equipped with a brake and a neutralization transmission body a crosspiece (116) used in the vehicle and connected to the projecting end of the valve; a transmission neutralization start valve means (166) establishing a cooperative action with said crosspiece; and a separate connection with said crosspiece. operator selection means (126, 162) for providing (124172), triggered by the braking stroke of the differential valve or neutralization of the transmitter by the crosspiece and by co-acting neutralization starter valve means; combined brake A collection that allows only key action strokes to be selected. 10. Valve-regulated power brake cylinder assembly, with retraction in the cylinder a control valve retractable in said chamber to a brake release control position; a differential piston (14) and a control valve (16) arranged in hydraulically opposed relationship across a loading chamber (96), said differential piston being arranged on a first side of said piston ( the piston on the second side (104) has an auxiliary brake spring (108); The engine can be forcibly pushed by the retractor, and the force is applied to the auxiliary brake spring. The opposite hydraulic relationship as previously mentioned is such that the differential separator (100) of the valve across the draw chamber is forced to move only until it is balanced by the latent force of the ring. are opposed by the second side (104) of the retractor so that, in the event of safety activation, they are effectively forced by the retraction chamber to retract the squares therein to the brake release adjustment position. A brake cylinder assembly comprising: 11. In the power brake assembly of the main brake plunger, remove the cylinder from the Consisting of a power gray cylinder with an auxiliary piston that is divided into extension and retraction parts, and - a control valve that can be retracted into the retraction chamber to the brake release adjustment position; located in said cylinders and slidably engaged with each other and opposed to each other across the retraction stiffener; towards The piston (14) energized by the auxiliary brake spring and the a brake plunger (24) actuated by a main spring; a brake plunger having a differential U (60) for actuating liquid through the load in the brake release direction to pull up the chamber, and a differential regulating valve with front = r; When relatively retracted to the brake release adjustment position in the retraction chamber, the valve adjustment load passage ( 102) and enters the differential chamber N, which is emptied by the brake plunger. the same amount of fluid is effectively transferred by the flow provided by the valve; and said intake block is directly connected to (143), and further said differential chamber is connected by a valving release passageway (132). , a refill water distribution reservoir (140), and said differential control valve is adapted to cause the valve to perform a braking stroke of the differential valve by an operator. make it possible. The differential section (100) of the differential valve, having an outwardly projecting end, is driven into engagement with one opposed differential piston to mechanically apply force and hollow into the retraction chamber. The valve causes the differential chamber to be retracted so as to leave a certain volume, and the valve passes from the differential chamber through the valve adjustment release passage (132).It is hollowed by the movement of the differential piston. 12. In the invention of claim 11, the auxiliary brake spring provides a power brake assembly comprising: The differential screw (14) 35 (35) has an auxiliary brake spring (108) in the spring chamber and is biased thereby, so that the valve In the regulating load path, the aforementioned transfer flow provided by the differential regulating valve (16) in the brake release regulating position is connected to the auxiliary brake spring. caused by the ring to move the differential piston, so that, due to said displacement, the entire amount of liquid that is displaced from the retraction plane by the differential piston enters the differential chamber hollowed out by the brake plunger. I will refill the entire capacity of The power brake assembly is adapted to be introduced by a valving load passage. 16. In a hydraulically operated master brake cylinder and hydraulically energized transfer transmission system, said transmission is configured to be hydraulically neutralized by transmission neutralization valve means during brake application. suitable for use, said system comprising a source of fluid to be pressurized and further comprising a section (58) located in the cylinder and moved by a differential pressure and for mechanically biasing the plunger in the direction of brake application. a slidable differential piston plunger (24) adjusted by a main spring (68) to A differential, liquid-releasable pressure chamber (60) in the brake chamber, in which the liquid pressure supplied from the source exerts a brake force opposite to the bias of the main spring. a pressure chamber adapted to be applied to the differential area in a releasing direction; 6 a differential valve (16) connected to said chamber and connected to a drain; at least one dull means (162); or 126), which is connected to said valve. means for manipulating the ligatures (172, 124) by which the system is operated to relieve pressure in the chamber and drain fluid, and also to mechanically bias the syringe effectively in the direction of braking. It means that there is no way to do it, and it has a strain. 14. In the invention of claim 13, the transmitter neutralizer has a stage (166, 170, N), and the dull means has a means for operating the connector (172) to the valve. The system is adapted to act as a brake as described, and is additionally connected to a valve means for neutralizing the transmitter, so that the system neutralizes the transmitter in addition to braking. Systems that are made to operate simultaneously as hydraulically operated. 15. In the invention according to claim 1, the R-dal means has a second pedal (126), and a second valve (126) connected to the chamber; 174) and before The second barrel has a first actuating means of the connector (124) to said differential valve to effect the braking action as described and to the second barrel (174). The connector (126) has a second operating means (126), and when the first operating means of the connector is inoperative, the A system characterized by causing a rake to act. 16. In the invention of claim 16, the barrel means has independent first (162) and second (126) R barrels, which are separately connected to the valve. (172, 124), whereby the system is alternately activated to relieve pressure in the chamber and mechanically bias the plunger in the direction of braking. A system that is designed to encourage you. 1Z In the invention of claim 16, the valve (16) has a handle (176), which handle has its own operating means for the connector (182) thereto, and A system whereby the system is operated alternately by a barrel or by a handle to release the pressure in the chamber to drain fluid and to mechanically bias the plunger in the direction of braking. 18. The assembly of the main brake plunger coupled with the power brake cylinder is controlled by the foot and through the forced stroke of the piston adjusted by the opposing spring. In a power braking method, the piston moves the cylinder in a sliding motion. dividing into a pulling and retracting section, and having in the cylinder an actuating valve adjacent to said piston and slidably associated therewith, and provided with a valve regulating load passage and a valve regulating release passage; Due to the action spring and valve regulating load passage. The main valve 38 is controlled by the differential chamber, which is filled with liquid through a channel, so that the plunger is controlled by the chamber directly into the cavity, and the differential chamber is controlled by means of a valve control release channel. Refill arrangement adapted to be connected A water reservoir is included, and the method described above causes the differential stone to have a pre-pressure fluid content stored in the latter by the first transfer. With respect to this, the entire amount of fluid that is displaced by the differential piston from the retraction chamber due to the transfer is introduced by the valve regulating load passage which is hollowed out by the differential piston and refills the entire amount of the differential chamber. To make it equal to the amount of N. Press the differential piston with your foot in the movement of hollowing out the cylinder, and the movement of the differential piston in the cylinder from the differential chamber through the valve adjustment release passage to the reservoir It is hollowed out so that it imparts the same amount of flow as the capacity of the draw tube. A method comprising: and . 19. Using the i-body source twice at pressures reaching its full output pressure, press the mask block. A method for power-operating a rake cylinder assembly, the brake cylinder assembly being The xylinder assembly is slidable for repeated strokes in the cylinder. The differential piston plunger is closed and the liquid reaction acting in the direction of brake release is released. having a force-transferring main piston area that provides a Zolandia area that is sensitive to the applied pressure and that can be mechanically and mechanically moved by the main spring and the applied pressure; The combined force acts in the direction of applying the brake, and in addition the differential piston plunger has a differential section which can move in pressure in the direction of releasing the brake, which is opposite to the combined force of the main spring and the main section pressure. a Therefore, a mutually exclusive next step is to apply the liquid pressure (Fig. 1, P2) from the source mentioned above to the main pressure transfer section MK at a pressure up to the full power pressure, thereby reducing the main spring and the main section. The combined force of pressure exerts a brake in the direction of brake application. The fluid pressure (Fig. 1 P1) from the source mentioned above is applied to the differential pressure transfer area at pressure up to full output, and the brake is released in the release direction to release the main sprocket. causing the combined pressure of residual pressure in the ring as well as in the main area to be overcome; 2. The invention according to claim 19, wherein the differential piston plunger is A differential chamber differential section operates in the conductor (along with an auxiliary drive in said assembly). Able to expand against the resistance force of a moving spring and collapse under the force of the spring. A retraction force that can be applied is provided, and a retraction force that can be crushed is applied to the source of pressure fluid on the outside. to allow the body to expand (92) and then maintain it under the force of the auxiliary spring, and to maintain the retraction stiffness under critical conditions and under the force of the spring. collapsing (102)g by displacing pressurized fluid in the differential chamber, forcing the differential chamber to fill the differential chamber and causing the differential piston plunger to drive the differential piston plunger in the brake release direction; Main stream adapted to overcome the combined forces of the pulling and main separation residual pressures; How to do it. 21. In the master brake cylinder assembly which has a main chamber and a differential chamber in the cylinder. and a slidable differential piston plunger (24) which acts in the brake release direction. liquid reaction pressure 1 (with a sensitive Zolandia area (40) and a fault-free main stage). a main piston which can be mechanically and hydraulically moved with a combined force in the direction of braking by a pulling (68) and by the pressure acting in the main pressure chamber (62) and on said main partition; Ward! a differential piston plunger (64) having a differential piston plunger (64); and a differential pressure lock (60) in the cylinder so that the supplied fluid pressure The combined force 14 of the pulling and the main area pressure present causes a differential pressure force to be applied in the opposite brake release direction to the differential area (58) of said slidable differential piston Zolandia. , the main pressure and the differential pressure (62, 60) are simultaneously drained (140, D) and applied in the direction of braking by the faultless main spring. A fault-free mechanical control of the applied motion can also produce a braking action. means (Fig. 6, 92.14B);