Braking system

Abstract

A hydraulic / mechanical braking system for a vehicle includes a cam (128) keyed to a driveshaft or driven wheel and at least two hydraulic cylinder assemblies (126, 129) including a cam follower (127). A hydraulic circuit (C) connects the hydraulic cylinder assemblies together. A master brake valve (113) controls the flow of fluid in the circuit. Actuation of the master brake valve (113) impedes the flow of fluid and thus impedes the reciprocating motion of the hydraulic cylinder assemblies, thereby forcing the cam follower against the cam to resist rotation. The cam (128) forms two opposing planes (142, 143) to provide an anti-lock braking system (ABS).

Description

[0001] open field In this specific context, this disclosure generally relates to braking systems for vehicles. Specifically, this disclosure relates to a hydraulic mechanical braking system that does not use conventional abrasive materials such as brake pads, brake shoes, brake discs, and brake drums, and therefore does not generate any particles (brake dust). Furthermore, the system does not use conventional brake calipers or driven cylinders. Another advantage of the braking system is that it is unaffected by wet weather (rain) because the system is completely sealed. The braking system of the present invention also includes an energy recovery system that utilizes energy from the flowing hydraulic fluid for other purposes. Invention Overview This invention provides a braking system for a vehicle, the braking system comprising: A cam, which is coupled to a drive shaft or a driven wheel for rotating together with said drive shaft or said driven wheel, the cam including a circumferential cam surface; At least two hydraulic cylinder assemblies, each assembly including a cylinder and a piston configured to reciprocate relative to each other, and a cam follower attached to the cylinder or piston and arranged to contact a cam surface, wherein rotation of the cam causes the cam follower and the cylinder or piston attached thereto to reciprocate relative to another piston or cylinder. A hydraulic circuit connects hydraulic cylinder assemblies together, through which hydraulic fluid flows as the cylinders and pistons of each assembly reciprocate relative to each other. The main brake valve is configured to control the flow of fluid around the hydraulic circuit; and An actuation system, comprising a user input device configured to actuate a main brake valve; The actuation of the main brake valve impedes the flow of fluid in the hydraulic circuit, thereby suppressing or preventing the relative reciprocating motion of the cylinder and piston of each component, as well as the reciprocating motion of each cam follower. This, in turn, causes the cam follower to suppress or prevent the rotation of the cam. The cam surface includes a first plane and a second plane, which are configured such that when the cam rotates, each cam follower simultaneously contacts the corresponding plane. The cam rotates about a rotational axis, and each hydraulic cylinder assembly is positioned along a reciprocating axis that intersects the rotational axis of the cam. The first and second planes are located radially opposite each other on the cam. The cam is symmetrical about an axis of symmetry that intersects the axis of rotation, such that the lowest point (perigee) and the highest point (apogee) of the cam are opposite each other, and the first plane and the second plane are located at the highest point and the lowest point of the cam, respectively.

[0003] Further advantageous features of the invention are set forth in the claims and description.

[0004] In this invention, a cam can be attached to a transmission system as a power output member (driveshaft), which advantageously engages, as needed, with at least two hydraulic cylinder assemblies (single-acting or double-acting cylinders), wherein cam followers (bearings, roller followers, etc.) are attached to the end of each hydraulic cylinder assembly (ideally, the cylinders are of equal size and used in pairs). The at least two hydraulic cylinders can be positioned radially spaced 180° apart (such that the centerline of the hydraulic cylinder assembly bisects the rotation center of the cam longitudinally) and operate relative to each other along the cam surface (i.e., when one hydraulic cylinder assembly can be fully extended, the other hydraulic cylinder assembly can be fully retracted), while the cam followers (roller followers) attached to the hydraulic cylinder assemblies contact (engage) with the cam surface.

[0005] The cam can be located in the middle between at least two hydraulic cylinder assemblies. When the drive shaft rotates, the cam rotates, which can be a bidirectional rotational motion in either direction (i.e., clockwise and counterclockwise), actuating the hydraulic cylinder assemblies so that the engaged hydraulic cylinder assemblies can perform bilinear motion (reciprocating motion).

[0006] In one embodiment, the cylinders (body tubes) of at least two hydraulic cylinder assemblies can be fixed relative to cams, so that each cam follower (bearing) is attached to the end of the piston (rod).

[0007] In another embodiment, the piston (rod) may be fixed relative to the cam, and the cam follower (bearing) is attached to the end of the cylinder (body tube) of each hydraulic cylinder assembly. As the cam rotates, the hydraulic cylinder assembly reciprocates, and hydraulic fluid (oil, lubricating fluid, low-viscosity fluid, etc.) within the hydraulic cylinder assembly is pumped into the hydraulic circuit (system piping network).

[0008] The hydraulic circuit is arranged such that hydraulic fluid flows from one hydraulic cylinder assembly to another through a series of check valves and fluid (oil) control valves.

[0009] Specifically, the main brake valve controls the flow of fluid (such as oil) in the hydraulic circuit.

[0010] The main brake valve can be actuated to restrict the flow of fluid to a desired level or extent. This restriction of fluid flow from one hydraulic cylinder assembly to the opposite second hydraulic cylinder assembly applies a force to the cam, causing the cam to slow its rotational movement. Thus, braking force is obtained on the driveshaft (output).

[0011] A second brake valve (manual brake valve) may also be included in the hydraulic circuit (C) (system piping network).

[0012] When braking force is not required, keeping the hydraulic cylinder assembly constantly engaged with the cam may be disadvantageous, as this would lead to unnecessary wear on the cam follower (bearing). Due to the continuous reciprocating motion of the hydraulic cylinder assembly, the cam and hydraulic cylinder assembly further exert inherent resistance on the rotating cam. Therefore, the braking system may include a separate second hydraulic circuit (high-pressure hydraulic system) for engaging and disengaging the merging double-acting hydraulic cylinder. The second hydraulic circuit may be arranged to be engageable or disengageable by actuation of the main brake valve and / or the second brake valve (respectively, the vehicle-related brake pedal or manual brake). The engagement and disengagement system may include a hydraulic pump, accumulator, pressure regulator, at least two single-acting hydraulic cylinders, a second hydraulic circuit (second piping network), at least one check valve, engagement valve, disengagement valve, oil, and oil sump.

[0013] The engagement and disengagement system can be configured such that when the brake pedal is moved to a minimum, the system is actuated and each cam follower (roller follower) attached to at least two hydraulic cylinder assemblies engages with the cam.

[0014] The invention is configured such that when user input (brake pedal or manual brake) is provided beyond the point where the roller follower engages with the cam, braking force is applied to the cam, thus actuating the master cylinder. Actuation of the master cylinder, in turn, actuates the master brake valve, which results in restriction of oil flow. This restriction of oil flow between the hydraulic cylinder assemblies results in braking force proportional to the degree of movement of the brake pedal.

[0015] The engagement and disengagement system comprises at least two single-acting hydraulic cylinders, each of which is securely fixed to the transmission housing along the longitudinal centerline of the double-acting hydraulic cylinder by a mechanical means. Actuation of the second brake valve or the main brake valve by a user input or a second user input engages the hydraulic cylinder assembly with the cam and cuts off the oil flow between the hydraulic cylinder assemblies. Therefore, the system is hydraulically locked and the cam cannot rotate.

[0016] Brief description The invention will now be described in detail by way of example only with reference to the accompanying drawings, in which: Figure 1 This is a schematic diagram of a portion of an example of a hydraulic mechanical braking system; Figure 2 It shows Figure 1 An enlarged view of the cam; Figure 3 It shows Figure 1 Enlarged view of part of the joint system; Figure 4 It shows Figure 1 An enlarged view of part of the separation system; Figure 5 It shows Figure 1 An enlarged view of a portion of a hydraulic cylinder assembly; Figure 6 It shows Figure 1 An enlarged view of a portion of the hydraulic circuit between the hydraulic cylinder assemblies; Figure 7 It shows Figure 1 Enlarged view of a single-acting piston section; Figure 8 It shows Figure 1 An enlarged view of the second brake valve section; Figure 9 It shows Figure 1 An enlarged view of the main brake valve section; Figure 10 It shows Figure 1 An enlarged view of a check valve; Figure 11 It shows Figure 1 An enlarged view of the accumulator; Figure 12 It shows Figure 1 Enlarged diagrams of sensors, signals, shut-off valves, and directional arrows are provided to aid reader understanding. Figure 13 It shows Figure 1 An enlarged view of a portion of a hydraulic cylinder assembly; Figure 14 This is a schematic diagram of a portion of another example of a hydraulic mechanical braking system; Figure 15 It shows Figure 1 For example, the cam rotates 45 degrees clockwise; Figure 16 It shows Figure 1 For example, the cam rotates 90 degrees clockwise; Figure 17 It shows Figure 1 For example, the cam rotates 135 degrees clockwise; Figure 18 It shows Figure 16 An example where the second brake valve engages; Figure 19 This illustrates a portion of yet another exemplary braking system, in which multiple hydraulic cylinder assemblies engage with cams; Figure 20 It shows Figure 1 The hydraulic mechanical braking system, in which the separation system valve is open; Figure 21 An enlarged view of a portion of yet another exemplary braking system with a single-acting hydraulic cylinder assembly is shown; Figure 22A schematic diagram of an energy recovery system for use with the present invention is shown; Figure 23 This is a schematic diagram of a portion of an embodiment of a hydraulic-mechanical braking system with an anti-lock braking system (ABS) according to the present invention; and Figure 24 It's a diagram. Figure 23 A diagram showing the functions of the braking system.

[0017] Detailed description This invention relates to a hydraulic mechanical braking system with an anti-lock braking system (ABS). See below for details. Figures 1 to 22 Describe the general characteristics and functions of the braking system. (Refer to...) Figure 23 and Figure 24 The specific features of the present invention are described.

[0018] Figure 1 A schematic diagram of an example hydraulic mechanical braking system is shown. (As shown) Figure 1 As shown, the system comprises three (three) independent hydraulic circuits, each with its own piping network (A, B, and C), which can be interconnected via shut-off valves to enable additional service functions. Assume the three hydraulic circuits are filled with fluids (oil, hydraulic fluid, low-viscosity fluid, lubricant fluid) (158) and completely bleed out, meaning all air has been expelled from the hydraulic circuits.

[0019] The braking system includes a cam (128). In this example, the cam (128) is a "heart-shaped" cam (128). The cam (128) can be coupled to a shaft, for example, the cam (128) can be coupled to a power transmission system (e.g., a transmission drive axle gearbox) via a spline hole (139) as a power output component (drive shaft or drive output). Alternatively, the cam (128) can be coupled to a rear wheel axle or a non-powered part of the driven wheel system. The cam (128) rotates, with an arrow indicating its direction of rotation (117). Figure 1 In the example, the cam rotates clockwise. The cam (128) is shown as having a center of rotation (140) and a cam surface (196).

[0020] The cam surface (196) engages with at least two cam followers (bearings, roller followers, etc.) (127). The cam followers (127) are optionally roller followers. The braking system also includes at least two hydraulic cylinder assemblies (126, 129). Each hydraulic cylinder assembly (126, 129) includes a cylinder (126, 129) and a piston (125, 130) configured to reciprocate relative to each other. Each cam follower is attached to the cylinder or piston and arranged to contact a cam, whereby rotation of the cam causes the cam follower and the attached cylinder or piston to reciprocate relative to another piston or cylinder. The cam follower may be attached to the cylinder via a clevis joint.

[0021] The hydraulic cylinder assemblies (126 and 129) can be positioned such that their longitudinal centerline (190) bisects the rotation center (140) of the cam, thereby ensuring that the cam follower (127) is arranged perpendicular to the cam surface (196) at the contact point or engagement point. The hydraulic cylinder assemblies (126 and 129) can be positioned 180° apart around the cam (128).

[0022] The hydraulic cylinder assemblies (126 and 129) are interconnected via a piping network (C) forming a hydraulic circuit. Additionally, the piping network (C) may include multiple check valves (104C, 204C, 110C, 210C). For example, as... Figure 1 As shown, a four-way directional control valve system is provided, which includes two check valves (104C, 204C) shown in the closed position and two check valves (110C and 210C) shown in the open position.

[0023] The cam (128) is rotatable clockwise. Preferably, the hydraulic circuit (C) of the braking system may also include a second brake valve (assembly) (105) (which is preferably the manual brake of the vehicle). Figure 1 In the diagram, the second brake valve (105) is shown in the open position, i.e., the manual brake (105) is in the closed position, while the main brake valve (assembly) (113) is in the partially open position. The hydraulic circuit (C) may also include an accumulator (102C), wherein the accumulator (102C) is fully pressurized to a preset desired pressure for the operating state of the braking system. A pressure regulating valve (100C) may be provided to ensure that the desired system pressure is not exceeded. Another check valve (188C) is in the closed position, and a shut-off valve (111C) is in the closed position.

[0024] Figure 1The first hydraulic cylinder assembly (126) shown on the left includes a piston (125), a cylinder, and a cam follower (127). Additionally, the first hydraulic cylinder assembly may also include a piston rod (123) and a cylinder head (124). The hydraulic cylinder assembly (126) may be located in a guide within the transmission housing (122) that allows the main body tube (cylinder) and its inlet / outlet pipes of the hydraulic cylinder assembly (126) to slide freely longitudinally along the longitudinal centerline (190) of the main body tube (cylinder). Similarly, Figure 1 The second hydraulic cylinder assembly (129) shown on the right includes a piston (130), a cylinder, and a cam follower (127). Additionally, the second hydraulic cylinder assembly may also include a piston rod (133) and a cylinder gland (131) in a guide located within the transmission housing (132). The guide in the transmission housing (132) allows the cylinder (body tube) of the hydraulic cylinder assembly (129) and its inlet / outlet pipes to slide freely longitudinally along the longitudinal centerline (190) of the cylinder (body tube).

[0025] The piston rod (123) of the first hydraulic cylinder assembly (126) may be securely or firmly attached at one end to the piston (125) within the hydraulic cylinder assembly (126), and at the other end to a single-acting piston (119). The single-acting piston (119) is part of a single-acting hydraulic cylinder (120). Similarly, the piston rod (133) of the second hydraulic cylinder assembly (129) may be securely or firmly attached at one end to the piston (130) within the hydraulic cylinder assembly (129), and at the other end to a piston (134), which may be part of another single-acting hydraulic cylinder (136).

[0026] For each of the hydraulic cylinder assemblies (126, 129), the single-acting hydraulic cylinders (120 and 136) can have the same dimensions and can be in a fully extended position, and are connected to each other via a piping network (A) to form another hydraulic circuit, namely a second hydraulic circuit (A). Furthermore, the piping network (A) may include at least one check valve (104A) closed in the closed position, an engagement valve assembly (115) in the closed position, a disengagement valve assembly (106) in the closed position, and an accumulator (102A) fully pressurized to a preset desired pressure, the at least one check valve (104A) being adjacent to the engagement valve assembly (115). The accumulator (102A) can be large enough to maintain a certain amount of oil at the desired pressure to activate the single-acting hydraulic cylinders (120, 136) when the hydraulic pump can be shut off, and also to compensate for changes in oil volume due to temperature variations. Figure 1As shown, the piping network (A) may also include a shut-off valve (107) in the open position, a check valve (110A) in the open position, a shut-off valve (111A) in the closed position, a hydraulic pump (103) that is activated and operates to provide the desired working system pressure, an oil pan (101), and a pressure regulating valve (100A) for ensuring that the desired system pressure is not exceeded.

[0027] In addition, the third hydraulic circuit (piping network) (B) can internally connect the master brake cylinder (112), the oil pan (101), the master brake valve (113), and the shut-off valve (111A) in the closed position.

[0028] One or more dashed circles (108) represent network pipes that intersect each other at right angles in the correlation diagram but are not connected (this only indicates where the pipes are not connected, and pipes crossing at 90 degrees is not a structural requirement). Small arrows (154) in the pipe network indicate the direction of oil flow in the correlation diagram. There are two dashed circles (118 and 137) whose centers are located at the rotation center (140) of the cam (128). Figure 1 As shown, circle (118) represents the circular path of the cam (128) at its maximum stroke, and circle (137) represents the circular path of the cam (128) at its minimum stroke. Figure 1 As shown, the small arrows in the parallel rows represent pressure heads (155).

[0029] The cam of the braking system may also include multiple tapped holes (138), wherein there may be eight (eight) equally spaced tapped holes (138) on the same pitch circle diameter (PCD), and the tapped holes (138) and the countersunk holes (141) may be used to position and fix the drive shaft relative to the driven wheel.

[0030] Cam (128) as Figure 1 As shown, when rotated clockwise, the apex (199) of the cam (128) is vertically positioned at the top, and the recess (198) is vertically positioned below, with the apex and recess being radially opposite each other on the central axis passing through the rotation center (140) of the cam.

[0031] The cam follower (127) attached to the hydraulic cylinders (126, 129) contacts (engages) the cam surface (196). The cam follower (127) is as follows: Figure 1The cylinder is attached to and arranged to contact a cam (128), the rotation of which causes the cam follower (127) and the cylinder attached thereto to reciprocate relative to the piston (125, 130). Both hydraulic cylinder assemblies (126, 129) are in the intermediate stroke position, i.e., half-retracted and half-extended. The pistons (119, 134) of the single-acting hydraulic cylinders (120, 136) are fully extended and in contact with the stop surfaces (200, 200) of the transmission housing guides (122, 132). The transmission housing guides (122, 132) serve as mechanical stops for the pistons (119, 134) to ensure that the pistons (119, 134) cannot extend further.

[0032] See below for reference. Figure 14 As further described, a cam follower (127) may be attached to a piston and arranged to contact a cam (128), whereby rotation of the cam (128) causes the cam follower (127) and the piston to which it is attached to reciprocate relative to the cylinder.

[0033] The single-acting hydraulic cylinders (120, 136) are fully extended and hydraulically locked in place by the closed check valve (104A), and the disconnect valve assembly (106) is also closed in the second hydraulic circuit (piping network (A)). In the piping network (A), the hydraulic pump (103) is active and pumps fluid around a portion of the circuit. The fluid flows along the small arrow (154) of the circuit to the disconnect valve assembly (106) in the closed position, and the disconnect valve assembly (106) is held under pressure by the hydraulic pump (103) or by a row of arrows on the indicating pressure head (155) to maintain the disconnect valve assembly (106) in the closed position. The pressure of the second hydraulic circuit (piping network (A)) can be controlled by the pressure regulator (100A).

[0034] If the hydraulic pump (103) is not activated, pressure from the accumulator (102A) can hold the release valve assembly (106) in the closed position. The release valve assembly (106) can be further held closed, mechanically connected to the brake pedal in the vehicle. This is merely a safety factor; if overpressure is generated in the hydraulic circuit (C) of the two hydraulic cylinders (126 and 129) due to braking, the resulting pressure differential will open the release valve assembly (106), and this overpressure may cause the two single-acting hydraulic cylinders to retract.

[0035] When the cam (128) is in the dynamic rotation stage as shown in the figure, the effect of the rotation of the cam (128) is that the cylinders (main tubes) of the two hydraulic cylinder assemblies (126, 129) are in the middle stroke position. A moment later, the rotation of the cam (128) will cause the cylinders of the double-acting hydraulic cylinders (126, 129) to reciprocate, and this will cause oil to flow in the hydraulic circuit (piping network) (C) in the direction shown by the arrow indicating the flow direction (154).

[0036] The flow generated by the reciprocating motion of the two hydraulic cylinder assemblies (126, 129) caused by the rotation of the cam (128) leaves the two double-acting hydraulic cylinders (126 and 129) and enters the hydraulic circuit (piping network) (C). In this case, the volume of fluid discharged from the hydraulic cylinder (126) is the volume of the annular space of oil surrounding the piston rod (123). The annular space of oil is defined between the piston (125), the inner end of the cylinder head (124), and the fluid volume between the piston (130) and the inner tube end of the double-acting hydraulic cylinder (129). Figure 1 As shown, the discharged fluid flows in the piping network (C) and is first directed to a closed check valve (104C). The check valve (104C) closes due to the pressure difference generated by the fluid flow, and the fluid bypasses the check valve (104C) and enters an open second check valve (110C). The second check valve (110C) opens due to the fluid flow pressure. From the second check valve (110C), the fluid continues to flow to the open second brake valve assembly (105) (in this case, the manual brake is in the closed position), and the fluid flows through the second brake valve assembly and can continue to flow to the main brake valve assembly (113).

[0037] At this stage, the master brake valve assembly (113) is partially opened due to the hydraulic pressure delivered by the master brake cylinder (112), which is indicated by the fluid flow from the master brake cylinder (112) through a conduit (indicated by an arrow indicating the direction of oil flow (154), which may be part of a conduit network (B). The hydraulic pressure delivered from the master brake cylinder (112) to the master brake valve (113) is controlled by the level of restriction created by the master brake valve (113) on the flow of oil.

[0038] The flow of fluid can originate from two hydraulic cylinder assemblies (126, 129). It is this restriction on the flow of fluid through the main brake valve (113) that establishes pressure and applies force to the fluid discharged from the hydraulic cylinder assemblies (126, 129), thereby controlling the rate at which the hydraulic cylinder assemblies (126, 129) can reciprocate. Controlling the rate of reciprocating motion causes the cam follower to apply resistance on the cam surface (196), thereby inhibiting or preventing the rotation of the cam (128). Since the cam (128) is coupled to the drive shaft, inhibiting or preventing the rotation of the cam also inhibits or prevents the rotation of the drive shaft, thereby providing braking force to the transmission.

[0039] The fluid flowing through the main brake valve assembly (113) has been restricted to a desired level or extent, and due to the pressure differential created by the restriction, the fluid flows out at a higher velocity. Furthermore, due to this restriction, the oil temperature rises through the resulting restriction, leading to an increase in oil volume. To compensate for this volume change, an accumulator (102C) can be included in the hydraulic circuit (piping network) (C). This change in fluid volume can occur downstream of the main brake valve (113). Due to the pressure differential, the downstream location of the main brake valve (113) is the low-pressure side. The accumulator (102C) functions not only to compensate for the volume change caused by temperature variations throughout the system but also to reduce cavitation occurring during fluid flow.

[0040] After the fluid has left the main brake valve (113), the fluid can be directed to the open check valve (210C), and the fluid can be directed back from the check valve (210C) to replenish the two hydraulic cylinder assemblies (126, 129). The total volume discharged is the total volume required to replenish the two hydraulic cylinder assemblies, and the hydraulic circuit (C) (piping network) allows this to be met because the two hydraulic cylinder assemblies (126, 129) have the same dimensions. This is because there is a difference between the volume of fluid discharged by the first hydraulic cylinder assembly (126) and the volume of fluid discharged by the second hydraulic cylinder assembly (129). Furthermore, the replenishment volume also has the same difference.

[0041] For example, the first hydraulic cylinder assembly (126) pumps fluid out of an annular space defined around the inner surfaces of the piston rod (123) attached to the piston (125) and the cylinder head (124). However, the volume of oil that may be needed in the chamber defined by the piston (125) and the end of the inner cylinder is larger due to the discharge volume of the piston rod (123). Furthermore, the second hydraulic cylinder assembly (129) pumps out the volume of oil defined by the piston (130) and the end of the inner cylinder.

[0042] The fluid may travel to the required volume of the double-acting hydraulic cylinder assembly (126) and the annular space volume discharged by the hydraulic cylinder assembly (126) supplements the annular space in the hydraulic cylinder assembly (129). This provides a balanced volume transfer, and the same will be true when the two hydraulic cylinder assemblies (126, 129) reciprocate in opposite directions and provide a balanced fluid volume transfer.

[0043] Figure 2 It shows Figure 1 An enlarged view of the cam (128). Figure 2 As shown, the cam (128) rotates about a center of rotation (140). The cam may include a splined bore (139). The cam may also include eight (eight) threaded holes (138) located on the same PCD, the eight threaded holes (138) being equally spaced, with the center of the PCD located at the center of rotation (140). The double-headed arrows indicate that the cam (128) can rotate in two directions (117). Figure 2 In the diagram, the vertex (199) is the highest point of the cam (128), and the recess (198) is the lowest point of the cam (128). The cam surface (196) extends around the cam (128). The dashed circle (118) represents the 360° path of the vertex (199) of the cam during rotation, and the dashed circle (137) represents the 360° path of the recess (198) of the cam during rotation.

[0044] Figure 3 It shows Figure 1 An enlarged view of a portion of the joining system (115). Figure 3 In the left-hand view, schematic diagram 115A shows the engagement valve assembly (115) in the open position. The engagement system may include a valve piston housing (149), a valve seat housing (148) with a valve seat (147), an uncompressed helical spring (144), a valve piston (145) with a valve face (146), two pressure seals (143 and 144), a retaining ring (116), and a lever (114). The lever shown has a pivot point (109) that is securely fixed relative to the piston valve housing (149) and a hole (150) to provide a connection between the lever and the brake pedal (not shown). Arrows indicate the direction of movement (151) of the lever (114) and the current position of the lever (114) in contact with the end of the valve piston (145) protruding from the valve piston housing (149), as shown in the diagram. Oil flows through the engagement valve assembly (115), the direction of oil flow indicated by arrows (154). Oil flow is delivered by a hydraulic pump (103, not shown) and supplies two single-acting hydraulic cylinders (120 and 136, not shown).

[0045] exist Figure 3In the right-hand view, schematic 115B shows the engagement valve assembly (115) in the closed position, so no oil flows through it. A lever (114) is actuated by the brake pedal via a connecting rod (not shown) connected in the bore (150) and in a different position (compared to engagement system 115A). In this configuration, the lever (114) pushes the valve piston (145), causing the valve face (146) to engage with the valve seat (147). This cuts off the oil supply through the valve piston (145). The coil spring (144) is compressed and assists in opening the valve when needed.

[0046] Figure 4 It shows Figure 1 A magnified view of a portion of the separation system (106). Figure 4 In the left-side view, schematic diagram 106A shows the separation valve assembly (106) in the open state. Figure 4 The separation valve assembly (106) is shown as including a valve piston housing (149), a valve seat housing (148) having a valve seat (147), an uncompressed helical spring (144), a valve piston (145) having a valve face (146), two pressure seals (143 and 144), a pin (153), and a lever (114). The lever (114) has a pivot point (109) that is securely fixed relative to the piston valve housing (149) and has a hole (150) to provide a connection to the brake pedal and / or a manual brake lever (not shown). An arrow indicates the direction of movement (151) of the lever (114), and the lever (114) has an elongated slot at its other end, and the current position of the lever (114) is shown as such, with the elongated slot positioned by the pin (153) to the end of the valve piston (145) that protrudes from the valve piston housing (149). Oil flows through the separation valve assembly (106), indicated by an arrow pointing in the direction of oil flow (154). Oil flow is delivered by two single-acting hydraulic cylinders (120 and 136, not shown) as they contract. Oil flows out of the separation valve assembly (106) and into the oil pan (101, not shown).

[0047] exist Figure 4 In the right-side view, schematic diagram 106B shows the separator valve assembly (106) in the closed position, so no oil flows through it. A lever (114) has been actuated by the brake pedal and / or the manual brake lever via a connecting rod (not shown) connected in the bore (150). The manual brake lever is in a different position (compared to separator system 106A) such that the lever (114) has pushed the valve piston (145), causing the valve face (146) to engage with the valve seat (147). This, in turn, cuts off the oil supply through the separator valve assembly.

[0048] A row of arrows indicates a pressure head (155) delivered by a hydraulic pump (103, not shown) in a chamber between the valve piston housing (149) and two pressure seals (143 and 144), one of which is on the valve piston (145). The other pressure seal is in the valve piston housing (149). This pressure head ensures a tight seal against any oil flow in the event of overpressure in the hydraulic circuit (A) associated with the release valve assembly (106). When the release valve is in the open position, the valve piston (145) cuts off the oil supply from the hydraulic pump (103, not shown), and a coil spring (144) assists the valve piston in moving away from the valve seat (147).

[0049] Figure 5 It shows Figure 1 An enlarged view of a portion of a hydraulic cylinder assembly (126). Figure 5 A longitudinal cross-sectional view of a double-acting hydraulic cylinder (126) is shown, which has a sized volume V1 (163), a sized volume V2 (167), an inlet / outlet conduit (159) for volume V1, an inlet / outlet conduit (160) for volume V2, a piston rod (123), a cylinder head (124), two pressure seals (143 and 143), a piston rod guide bushing (161), a piston (125), a pin (150), a U-joint (162), and a roller follower (127) including a bearing roller (164), an inner bearing ring (166), and an outer bearing ring (165). All double-acting hydraulic cylinders (126, 129) used herein may have the same specifications and dimensions. In particular, each hydraulic cylinder assembly in each pair of hydraulic cylinder assemblies preferably has the same specifications and dimensions. Volume V1 (163) (using Figure 5 The dimension marked above is the volume defined by the inner diameter (bD) and the length of the annular space (lA), minus the volume of the piston rod with diameter (rD) and length of the annular space; therefore, V1 = π(0.5bD). 2 ×lA- π(0.5rD) 2 ×lA; The volume V2 (167) is simply: V2 = π(0.5bD) 2 ×tC.

[0050] Figure 6 It shows Figure 1 Enlarged view of a portion of the hydraulic circuit (C) between the hydraulic cylinder assemblies (126, 129). Figure 6A longitudinal cross-sectional view of two (two) double-acting hydraulic cylinders (126, 129) is shown, which are cross-connected by a piping network (C) without any valves. This is to illustrate how the oil balance shifts when the cylinders reciprocate (assuming the system is sealed and pressurized, and the temperature will remain constant to provide a constant oil volume).

[0051] Assume two identical double-acting hydraulic cylinders (126, 129) are cross-connected by a piping network (C). When double-acting cylinder (126) is fully retracted (compressed) and double-acting cylinder (129) is fully extended, the piping network (C) is filled and sealed with oil. It can then be easily seen that if the piston rod (133) of the extended double-acting cylinder (129) is pushed into the middle (intermediate stroke) position of the cylinder, then double-acting cylinder (126) will automatically present the same intermediate stroke position. This is due to the oil being discharged from one cylinder to the other. If the piston rod (133) is fully pushed into one cylinder (full stroke), then the piston rod (123) will be fully extended in the other cylinder.

[0052] Turn now Figure 7 , Figure 7 It shows Figure 1 Enlarged views of portions of the single-acting pistons (120, 136). The single-acting piston in schematic A is a longitudinal cross-section of a single-acting hydraulic cylinder (120) having a piston (119), a pressure seal (143), an outlet pipe (174), and an inlet pipe (175). The arrow indicates the direction of movement (151) of the piston to its fully extended position. The single-acting piston in schematic B shows the same cylinder in its fully retracted position, with the arrow indicating the direction of movement (151).

[0053] The single-acting piston in schematic diagram C is a longitudinal cross-section of a single-acting hydraulic cylinder (136) having a piston (134), a pressure seal (143), an inlet / outlet pipe (176), and an arrow indicating the direction of movement (151) of the piston to its fully extended position. The single-acting piston in schematic diagram D shows the same cylinder in its fully retracted position, with the arrow indicating the direction of movement (151).

[0054] Figure 8 It shows Figure 1 An enlarged view of a portion of the second brake valve (105). Figure 8In the left-hand view, schematic diagram 105A shows a manual brake valve assembly (105) in the open position, which has a valve piston housing (149), a valve seat housing (148) with a valve seat (147), an uncompressed coil spring (144), a valve piston (145) with a valve face (146), a pressure seal (143), a retaining ring (116), and a lever (114). The lever (114) includes a pivot point (109) that is securely fixed relative to the piston valve housing (149) and has a hole (150) to provide a linkage to the manual brake lever (not shown). The linkage configuration also includes connections to the engaging valve assembly (115) (not shown) and / or the disengaging valve assembly (106) (not shown). The arrow indicates the direction of movement (151) of the lever (114), and the current position of the lever is shown as contacting the end of the valve piston (145) protruding from the valve piston housing (149), wherein oil flows through the manual brake valve assembly (105) as indicated by the arrow indicating the direction of oil flow (154). Oil flow is delivered by the reciprocating motion of two (two) double-acting hydraulic cylinders (126 and 129, not shown). The arrow indicates the direction of movement (151) of the valve piston with the aid of the coil spring (144) to bring the valve piston to the open position.

[0055] exist Figure 8 In the right-hand view, schematic 105B shows the manual brake valve assembly (105) in the closed position, so no oil flows through it. A lever (114) is actuated by a manual brake lever (not shown) via a connecting rod (not shown) connected in a hole (150) and is in a different position (compared to manual brake system 105A). The position of the lever (114) is such that it has pushed the valve piston (145), causing the valve face (146) to engage with the valve seat (147). This cuts off the oil supply through the manual brake valve assembly. The coil spring (144) is compressed and assists in opening the valve when needed.

[0056] Turning Figure 9 , Figure 9 It shows Figure 1An enlarged view of a portion of the main brake valve (113). Schematic diagram 113A shows the main brake valve assembly (113) in the open position, which has a valve piston housing (149), a valve seat housing (148) with a valve seat (147), an uncompressed helical spring (144), a valve piston (145) with a valve face (146), and a pressure seal (143). Arrows indicate the direction of movement (151) of the valve piston (145), through which oil flows through the main brake valve assembly (113) as indicated by arrows indicating the direction of oil flow (154). Oil flow is delivered by the reciprocating motion of two (two) double-acting hydraulic cylinders (126 and 129, not shown). Arrows indicate the direction of movement (151) of the valve piston assisted by the helical spring (144) to position the valve piston in the open position. The outflowing oil returns to the supplementary side of the two double-acting hydraulic cylinder assemblies (126, 129; not shown).

[0057] The valve piston housing (149) is connected to the master brake cylinder (112; not shown) at the opposite ends of the valve piston face (146). A set of three (triple) small arrows indicating the direction of oil flow (154) indicates the return of oil from the chamber between the valve pistons (145). The valve piston housing (149) is sealed to the master brake cylinder (112; not shown) by a pressure seal (143).

[0058] Schematic diagram 113B shows the master brake valve assembly (113) in the closed position, thus no oil flows through it. The master brake valve assembly (113) has pushed the valve piston (145) so that the valve face (146) engages with the valve seat (147), as indicated by the arrows indicating the direction of movement (151) of the valve piston (145). This cuts off the oil supply through the master brake valve assembly. The coil spring (144) is compressed and assists in opening the valve when needed. When the valve piston housing (149) is connected to the master brake cylinder (112; not shown) at the opposite end of the valve piston face (146), a set of two (two) small arrows indicating the direction of oil flow (154) indicate the oil entering the chamber from the master brake cylinder (112; not shown). Oil enters between the valve piston (145) and the valve piston housing (149), which are sealed by the pressure seal (143). Oil from the master brake cylinder (112; not shown) causes the valve piston to move toward the valve seat (147), with the arrow indicating the direction of movement (151). The amount of oil entering the chamber determines the degree of movement of the valve piston toward the valve seat (147). The degree of movement, depending on the distance between the valve face (146) and the valve seat (147), restricts the oil flow between the valve face (146) and the valve seat (147), which determines the amount of braking force delivered to the rotary cam (128; not shown).

[0059] Figure 10 It shows Figure 1 Enlarged view of a check valve. Reference numerals 104 and 110 denote valves, but the details shown in these views apply to... Figure 1 All check valves. Specifically, these views are: Plan view of baffle plate (177).

[0060] The baffle plate (178) is along the cross section of BB.

[0061] Cross-section of a one-way valve housing (181) with a hammer lip (184).

[0062] A plan view of the cross section of the one-way valve housing (181) along AA.

[0063] A plan view of a three-finger leaf spring (179) and a side view of a three-finger leaf spring (180).

[0064] The cross-section (189) of the assembled check valve has a check valve body (181) in which a baffle plate (178) and a three-finger leaf spring (180) are forged together with a hammer lip (184).

[0065] A plan view (194) of the cross section of the complete one-way valve assembly along AA, which has a forged lip (183), a baffle plate (177) and a three-finger leaf spring (179).

[0066] The cross section (104) of a closed check valve (closed in its normal state) with an inlet pipe (175) and an outlet pipe (174) is fully constructed.

[0067] A cross-section (110) of an open check valve with an inlet pipe (175) and an outlet pipe (174); wherein an arrow indicates the direction of oil flow when the valve is open.

[0068] Figure 11 It shows Figure 1 An enlarged view of an accumulator (applicable to 102A or 102C) showing a floating piston (186) with a pressure seal (143), a Schrader valve (185), an air chamber (187), and oil (158) separated from the air chamber (187) by the floating piston (186) with the pressure seal (143). Accumulator technology has been around for many years and is currently deployed in the hydraulic industry and is common practice, so no further discussion is needed.

[0069] Figure 12 It shows Figure 1 Enlarged diagrams of sensors, signals, shut-off valves, and directional arrows are provided to aid reader understanding: Linear or curved arrows indicating the direction of movement (151).

[0070] Arrow (154) indicating the direction of oil flow.

[0071] A row of arrows indicating the pressure head (155).

[0072] Hydraulic pump (103).

[0073] Multiple intersecting pipes (108).

[0074] Closed shut-off valve (111).

[0075] The closed valve (107) is open.

[0076] Pressure regulating valve (suitable for 100A and 100C) and The master brake cylinder (112) has a pipe in the pipe network (B).

[0077] Figure 13 It shows Figure 1 Enlarged view of a portion of a hydraulic cylinder assembly (129, 135). Figure 13 In the figure, schematic diagram 135A shows a longitudinal cross-section of a double-acting hydraulic cylinder having a piston rod (133), an inlet / outlet pipe (160) for volume V2, an inlet / outlet pipe (159) for volume V1, and the right side portion of the transmission housing that acts as a linear guide (132). Figure 1 (as shown in the image).

[0078] Schematic diagram 135B shows a side view of a double-acting hydraulic cylinder (129) with a piston rod (133) and a cylinder head (131). The cylinder head (131) is housed in a transmission housing (132) with a sliding clearance (195), wherein the double-acting hydraulic cylinder (129) has an inlet / outlet conduit (159) for a volume V1. The double-acting hydraulic cylinder (129) can reciprocate by the action of a rotary cam (128, not shown) or by the action of a single-acting hydraulic cylinder (136, not shown) during its extension and retraction.

[0079] Figure 14 This shows another example of a braking system. It is typically similar to... Figure 1However, the following changes are made: The cam (128) rotates counterclockwise. The roller followers (127 and 127) attached to the U-joints (162 and 162) are attached to the end of the piston rod (123 and 133), instead of the end of the body tube of the double-acting hydraulic cylinder (126 and 129). The ends of the body tubes of the double-acting hydraulic cylinder (126 and 129) are attached to the pistons (119 and 134) of the single-acting hydraulic cylinder (120 and 136), respectively.

[0080] Return to Figure 1 The example shown, Figure 15 It shows the relationship with Figure 1 Compared to the cam (128) in the middle, the cam (128) has been rotated 45° (degrees) clockwise. This rotation of the cam (128) then causes the two double-acting hydraulic cylinders (126 and 129) to move to the right, as indicated by the two arrows (151 and 152) indicating the direction of movement, thereby pumping oil in the circuit of the piping network (C), with Figure 1 No other changes have occurred.

[0081] Figure 16 It shows the relationship with Figure 1 Compared to the cam (128) in the middle, the cam (128) has rotated 90° (degrees) clockwise. The rotation of the cam (128) then causes the two double-acting hydraulic cylinders (126 and 129) to move to the right, as indicated by the arrows pointing in the direction of movement (151). Therefore, oil is pumped in the circuit of the piping network (C), with Figure 1 In contrast, no other changes occurred. At this stage, the double-acting hydraulic cylinder (126) is fully extended and the double-acting hydraulic cylinder (129) is fully retracted.

[0082] Figure 17 It shows the relationship with Figure 1 Compared to the cam (128) in the circuit, the cam (128) has rotated 135° (degrees) clockwise. This rotation of the cam (128) subsequently causes two (two) double-acting hydraulic cylinders (126 and 129) to move to the left, as indicated by the arrows pointing in the direction of movement (151). Therefore, by pumping oil in the circuit using the piping network (C), it can be seen that, compared to... Figure 1 In contrast, the flow of pumped oil changes direction in section C of the piping network. Other changes that have occurred include the change in the flow direction of the pumped oil. Figure 1 right side and Figure 17 The state of the four (four) check valves clustered together below the accumulator in the pipeline network (C) has changed.

[0083] It is easy to see that, compared with Figure 1 and Figure 17The direction of the oil pumped out by the two (two) double-acting hydraulic cylinders (126 and 129) in the piping network (C) is irrelevant. The pumped oil always passes through a set of four (four) check valves before traveling to the manual brake valve assembly (105) and from there to the master brake valve (113). Then, as depicted, the oil returns from there to the two (two) double-acting hydraulic cylinders (126 and 129) through a set of four (four) check valves.

[0084] When cam (128) is in Figure 16 When the two double-acting hydraulic cylinders (126 and 129) are in the position where one is fully retracted and the other is fully extended, a change in the direction of oil flow will always occur. This is in Figure 16 In the case of the double-acting hydraulic cylinder (126), the double-acting hydraulic cylinder (129) is fully extended and fully retracted. Regardless of the orientation of the cam (128) at 180°, later the two double-acting hydraulic cylinders (126 and 129) will cause the double-acting hydraulic cylinder (126) to fully retract and the double-acting hydraulic cylinder (129) to fully extend.

[0085] The four (quadruple) check valves (104C, 204C, 110C and 210C) in this group are actuated by the differential pressure caused by the pumping action of oil by two (two) double-acting hydraulic cylinders (126 and 129) in the piping network (C).

[0086] When the cam (128) is in its rotation Figure 16 At the position shown, the oil velocity is zero. For every 180° (degrees) rotation of the cam (128), the two double-acting hydraulic cylinders (126 and 129) must change their direction of travel, thus pumping oil at a velocity in the form of a given sine wave. This is the preferred form, a factor well understood in mathematics and applied mechanics, and requires no further discussion in this paper. In other examples, this form can have different wave forms for the velocity of the reciprocating piston.

[0087] Figure 18 It shows Figure 16 In the example, the second brake valve engages. Figure 18 In the middle, the cam (128) is in a stationary position, with the two single-acting hydraulic cylinders (120 and 136) fully extended. The left double-acting hydraulic cylinder (126) is also fully extended, and the right double-acting hydraulic cylinder (129) is fully retracted. In this configuration, the roller followers (127 and 128) of the hydraulic cylinders engage with the cam surface (196), and there is no oil flow in the pipe network (C).

[0088] A set of four (quadruple) check valves (104C, 204C, 110C, and 210C) in the piping network (C) are in their closed positions because there is no oil flow or pressure differential in the circuit. The manual brake valve assembly is in the closed position and will not allow oil to travel through it, resulting in hydraulic locking of the oil in the piping network (C) and the two (double) double-acting hydraulic cylinders (126 and 129), and therefore the cam (128) cannot rotate in either direction. The linkage between the levers (114) of the manual brake valve assembly actuates and closes the lever (114) on the release valve assembly (106), which is also connected to and actuates the lever (114) on the engagement valve assembly (115), thereby opening the internal valve to allow oil from the hydraulic pump (103) or from the accumulator in the piping network (A) to fill the two single-acting hydraulic cylinders (120 and 136) under pressure to fully extend the two single-acting hydraulic cylinders; thus, the manual brake is now in the ON position.

[0089] Figure 19 This is a partial example showing multiple hydraulic cylinder assemblies engaged with a cam. Figure 19 In this context, a possible example is that one or more hydraulic cylinder assemblies can be deployed around a cam (128) having a rotation center (140) and a cam surface (196).

[0090] There are four (four) pairs of double-acting hydraulic cylinders, arranged radially opposite each other: pairs A1 and A2, B1 and B2, C1 and C2, and finally D1 and D2. In this configuration, with... Figure 1 Compared to a system using only one pair of double-acting hydraulic cylinders, this configuration provides a much stronger braking force. This configuration increases the lifespan of the cam (128) and the double-acting hydraulic cylinders (A1, A2, B1, B2, C1, C2, D1, and D2), while applying less mechanical stress to achieve the same braking force compared to a system using only one pair of double-acting hydraulic cylinders. A similar arrangement with more than one pair of single-acting hydraulic cylinder assemblies can also be provided.

[0091] Figure 20 It shows Figure 1 The hydraulic mechanical braking system, in which the release system valve is open. Figure 20In this configuration, the braking system of the present invention is in a passive state, with the cam (128) rotating in either direction, the double-headed arrow indicating the direction of rotation (117), and the pistons (119, 134) fully retracted (retracted) in the cylinders (120, 136), respectively. The brake engagement valve assembly (115) is in the closed position, the release valve assembly (106) is in the open position, the manual brake valve assembly (105) is in the open position, the master brake valve (113) is in the open position, and the two double-acting hydraulic cylinders (126, 129) are in their intermediate stroke positions. In this configuration, the hydraulic cylinders (126, 129) have been pushed by the rotating cam (128) to reach this position where resistance is minimal. Oil from the two single-acting hydraulic cylinders (120 and 136) returns to the oil pan (101) through the open release valve assembly (106).

[0092] When the brake pedal (not shown) is gently pressed, it closes the release valve assembly (106) and opens the lever (114) of the lever (114) connected to the engagement valve assembly (115). The open valve assembly (115) allows oil from the hydraulic pump to be delivered to two single-acting hydraulic cylinders (120 and 136) to push two double-acting hydraulic cylinders (126 and 129) toward the cam (128) until the roller followers (127 and 128) engage the cam surface (196). Any additional pressing of the brake pedal will generate braking force on the rotating cam (128) by restricting the flow of oil in the master brake valve (113).

[0093] exist Figure 21 The diagram shows an enlarged view of a portion of another example, where each hydraulic cylinder assembly includes a single-acting piston instead of a double-acting piston as in the previous example. This portion of the braking system shows a cam (128) engaging the drive shaft, two hydraulic cylinder assemblies, a main brake valve (113), multiple check valves (104C, 204C, 110C, 210C), and a second brake valve (105). The hydraulic circuit connects the hydraulic cylinder assemblies, the main brake valve (113), the multiple check valves (104C, 204C, 110C, 210C), and the second brake valve (105). Therefore, this generally corresponds to the hydraulic circuit (C) in the previous example. In use, Figure 21 The braking system can be used in conjunction with engagement and disengagement systems and hydraulic circuits (A) and (B), largely as in the aforementioned examples, but for clarity they are omitted in this figure.

[0094] This example is similar to, for example Figure 1The main difference between the aforementioned examples is that the hydraulic cylinder assembly in this example includes pistons (125, 130) and cylinders (126, 129) arranged to provide a single chamber. Therefore, the hydraulic cylinder assembly in this example is single-acting rather than double-acting. Cam followers (127) are attached to the pistons (125, 130) of each assembly, and these pistons will reciprocate together relative to the corresponding cylinders (126, 129) of each assembly. As shown in the previous examples, hydraulic fluid flows through the circuit when the engagement system is actuated and the cam follower (127) contacts the cam as the cam rotates, and when the cylinders (126, 129) and pistons (125, 130) of each assembly reciprocate relative to each other. The master brake valve (113) is configured to control the flow of fluid around the hydraulic circuit, and the actuation of the master brake valve (113) impedes the flow of fluid in the hydraulic circuit, such that the relative reciprocating motion of the cylinders (126, 129) and pistons (125, 130) of each component and the reciprocating motion of each cam follower (127) are inhibited or stopped, thereby the cam follower (127) subsequently inhibits or stops the rotation of the cam (128).

[0095] exist Figure 21 In the diagram, each cam follower (127) is positioned relative to the cam (128). Each hydraulic cylinder assembly is in its maximum retracted or extended position. The hydraulic fluid in the hydraulic fluid circuit is shown flowing counterclockwise (154). Both the master brake valve (113) and the second brake valve (105) are in the open position, so the flow of hydraulic fluid is unobstructed, and the hydraulic cylinder assemblies do not exert a restrictive force on the cam (128). Continuous rotation of the cam (128) will cause the piston (125) shown on the left side of the diagram to move into its cylinder (126), and the piston (130) shown on the right side to move out of its cylinder (129). This will reverse the flow direction of the hydraulic fluid in the circuit. Multiple check valves (104C, 204C, 110C, 210C) in the hydraulic circuit are configured to ensure that the hydraulic fluid always enters the master brake valve (113) in the same direction.

[0096] Despite Figure 21 Not shown, but as described above, the engagement and disengagement system is typically connected to the hydraulic cylinder assembly. In this case, the cylinders (126, 129) of each assembly serve as single-acting pistons for the engagement and disengagement system (115, 106), which are actuated by fluid in the second hydraulic circuit (A). When the engagement and disengagement system (115, 106) is engaged via a user-input actuation system, the hydraulic fluid in the second hydraulic circuit (A) thus causes the hydraulic cylinder assembly to contact the cam (128).

[0097] Figure 22A schematic diagram of an energy recovery system that can be used with the present invention is shown. This can be used with any construction of the braking system described above and integrated within a hydraulic circuit (C). The energy recovery system allows energy in the hydraulic fluid flowing in the circuit to be used for other purposes. Specifically, kinetic energy can be used to generate electricity. Furthermore, heat can be extracted from the fluid.

[0098] Figure 22 The master brake valve assembly (113) in a partially open state is shown. As described above, the master brake valve assembly has a valve piston housing (149), a valve seat housing (148) with a valve seat (147), a coil spring (144) shown here in a partially compressed state, a valve piston (145) with a valve face (146), and a pressure seal (143). The position of the valve face (146) and therefore its proximity to the valve seat (147) is regulated by pressure applied by the master brake cylinder (112, indicated by a circle with the number 112), which is connected to the valve piston housing (149) via a conduit. Fluid (149) pushed into the valve piston housing by the master brake cylinder pushes the valve piston (145) with the valve face (146) closer to the valve seat (147). Figure 22 In the middle, hydraulic fluid passes through the main brake valve assembly (113), as indicated by the arrow indicating the flow direction (154); the fluid flow is delivered by the reciprocating motion of two hydraulic cylinder assemblies, which are schematically shown here by the uppermost circles containing the numbers 126 and 129.

[0099] Fluid exits the main brake valve assembly (113) and enters a conduit connected to an impeller housing (192) with an impeller (191) having an impeller output shaft bore (197). Arrow (117) indicates the direction of rotation of the impeller (191). When fluid flow in the circuit is restricted by moving the valve face (146) closer to the valve seat (147), the fluid temperature rises and it exits at a higher speed capable of driving the impeller (191) to rotate. Kinetic energy can be recovered using this rotational or turning motion by connecting the impeller (191) to a power generation device such as an AC generator or DC generator (dynamo). For example, this can be used for lighting or other electrical systems in vehicles.

[0100] Furthermore, the fluid, still at an elevated temperature, exits the impeller housing (192) via a pipe connected to the heat exchanger (193). Heat can be extracted from the fluid for use in other systems. For example, this can be used to power ammonium hydrogen absorption cooling systems (which are well-known and have existed for many years and are still deployed in industry, and therefore require no further discussion), supplementing air conditioning systems in vehicles or refrigeration systems in commercial vehicles carrying frozen or chilled foods. The fluid exits the heat exchanger (193) and returns to the hydraulic cylinder assembly, as indicated by the bottom circle containing the numbers 126 and 129.

[0101] Therefore, in various examples, the braking system includes a cam (128), at least two hydraulic cylinder assemblies (126, 129), a hydraulic circuit (C), and a master brake valve (113). The cam (128) is coupled to a drive shaft to rotate therewith. Each hydraulic cylinder assembly (126, 129) includes a piston (125, 130) and a cam follower (127). The piston (125, 130) and the hydraulic cylinder (126, 129) reciprocate relative to each other. The cam follower (127) is attached to either the hydraulic cylinder (126, 129) or the piston (125, 130). The hydraulic circuit (C) connects at least two hydraulic cylinder assemblies and the master brake valve. The hydraulic circuit (C) allows fluid to flow between the at least two hydraulic cylinders (126, 129) and the master brake valve (113). The master brake valve (113) is configured to control the flow of fluid around the hydraulic circuit (C). The actuation of the master brake valve (113) restricts the flow of fluid in the hydraulic circuit (C). This restriction of fluid in the hydraulic circuit (C) limits the reciprocating motion of the hydraulic cylinders (126, 129) and pistons (125, 130). This restriction of the reciprocating motion of the hydraulic cylinders (126, 129) and pistons (125, 130) applies a braking force from the cam follower (127) to the cam (128). This braking force limits the rotation of the cam (128), and thus limits the rotation of the drive shaft. The braking system also includes an energy recovery system configured to transfer energy from the hydraulic fluid flowing in the hydraulic circuit for power generation and / or heat recovery.

[0102] As the drive shaft rotates, the cam (128) will also rotate as long as the master brake valve (113) does not restrict the flow in the hydraulic circuit (C). From the actuation point of the master brake valve (113) to the engagement point between the valve piston (145) and the valve seat (147), the flow of fluid through the valve becomes increasingly obstructed. The obstruction of fluid flow in the valve causes the fluid flow in the hydraulic circuit (C) to be restricted and eventually completely blocked. When the input to the master brake valve (113) is removed, the restriction or blockage of fluid flow is removed.

[0103] Preferably, the invention includes an engagement and disengagement system that ensures the cam follower engages the cam only when braking is required and disengages from the cam when braking is not required.

[0104] When braking is required and input is provided to the master brake valve (113), the engagement system (115) is actuated to move the cam follower (127) into engagement with the cam (128). When braking is not required and there is no input to the master brake valve, the disengagement system allows the cam follower (127) to disengage from the cam (128).

[0105] The engagement and disengagement system comprises a single-acting piston acting on each hydraulic cylinder assembly. When the engagement system is operated, the single-acting piston forces each hydraulic cylinder assembly toward the cam (128) and keeps the cam follower (127) in contact with the cam (128). When the disengagement system is operated, the single-acting piston is released and allows the cam (128) to rotate to push each hydraulic cylinder assembly away to its furthest position, thereby disengaging the cam follower (127) from the cam (128).

[0106] Figure 23 A braking system according to the invention is illustrated. In this braking system, the form of the cam (128) is modified to provide an anti-lock braking system (ABS). Other features of the braking system are as described above, and the modified cam (128) can be used in any of the foregoing examples. The function of ABS is to prevent the wheels from locking up during braking, thereby maintaining traction frictional contact with the road surface and allowing the driver to maintain more control over the vehicle.

[0107] Specifically, in this invention, the cam surface (196), that is, the circumferential surface of the cam (128) that contacts the cam follower (127), forms two planes (142, 143). These two planes (142, 143) are arranged such that the two cam followers (127) will simultaneously contact the corresponding planes (142, 143).

[0108] As described above, the cam (128) rotates about the axis of rotation, and each hydraulic cylinder assembly (126, 129) is positioned along a reciprocating motion axis intersecting the axis of rotation. In other words, the two hydraulic cylinder assemblies (126, 129) are positioned relative to each other, and the cam follower (127) contacts the cam (128) at radially opposite positions. Therefore, in this arrangement, planes (142, 143) are arranged at radially opposite positions on the cam (128).

[0109] The cam (128) is symmetrical about an axis of symmetry intersecting the axis of rotation, such that the lowest point of the cam and the highest point of the cam are opposite each other. Planes (142, 143) are formed at the highest and lowest points. Therefore, the cam (128) can be considered as a heart-shaped cam as described above, but the cam has been truncated at the top and bottom of the heart shape.

[0110] As the cam (128) rotates, the movement of each cam follower (126, 129) can be illustrated as a sine wave, as shown below. Figure 24 As shown. For example Figure 1 The heart-shaped cam shown will provide a true sine wave, where each peak and trough of the waveform represents a point where zero braking force is applied to the cam (128). In this invention, the peaks and troughs of the waveform are truncated by providing planes (142, 143) on the cam (128), as... Figure 24 The shaded area in the image shows the amount by which the waveform amplitude is truncated, T. L It provides the time period t during which no braking force is applied. x Since the cam (128) rotates multiple times per second, this results in multiple cycles t per second without braking force. x This provides the effect of an anti-lock braking system, preventing vehicle wheels from locking up and the vehicle from slipping.

[0111] By changing the proportion of the length of the planes (142, 143) to the total length of the cam surface (196), the amount by which the waveform amplitude is truncated can be changed, and this in turn changes the period t of zero braking force. x Therefore, by modifying the construction of the cam surface (196), an anti-lock braking system can be provided that can be adjusted to suit different vehicles without requiring the complex electronic controls used in conventional ABS technology. Since the system is entirely mechanical, it is immune to electronic malfunctions.

[0112] The braking system of this invention is independent, requires no external power source, and includes the necessary control elements for a functional braking system suitable for various vehicles. The hydraulic-mechanical braking system of this invention is integrated into the transmission, thus improving the steering sensitivity of front-wheel-drive vehicles. The system is unaffected by wet weather, and because it does not involve friction materials that impede rotation (brake pads and discs), it has environmental advantages as it does not generate polluting dust.

Claims

1. A braking system for a vehicle, comprising: A cam, coupled to a drive shaft or a driven wheel for rotating together with the drive shaft or the driven wheel, the cam including a circumferential cam surface; At least two hydraulic cylinder assemblies, each hydraulic cylinder assembly including a cylinder and a piston configured to reciprocate relative to each other, and a cam follower attached to the cylinder or the piston and arranged to contact the cam surface, wherein rotation of the cam causes the cam follower and the cylinder or the piston attached thereto to reciprocate relative to the other of the piston or the cylinder; A hydraulic circuit that connects the hydraulic cylinder assemblies together, through which hydraulic fluid flows as the cylinders and pistons of each hydraulic cylinder assembly reciprocate relative to each other; A main brake valve configured to control the flow of fluid around the hydraulic circuit; as well as An actuation system includes a user input device configured to actuate the main brake valve; Wherein, the actuation of the main brake valve impedes the flow of fluid in the hydraulic circuit, thereby suppressing or preventing the relative reciprocating motion of the cylinder and the piston of each hydraulic cylinder assembly and the reciprocating motion of each cam follower, thereby suppressing or preventing the rotation of the cam by the cam follower. The cam surface includes a first plane and a second plane, which are configured such that when the cam rotates, each cam follower simultaneously contacts the corresponding plane. The cam rotates about a rotation axis, and each hydraulic cylinder assembly is positioned along a reciprocating motion axis intersecting the rotation axis of the cam, with the first plane and the second plane located at radially opposite positions on the cam; and The cam is symmetrical about an axis of symmetry intersecting the axis of rotation, such that the lowest point of the cam and the highest point of the cam are opposite each other, and the first plane and the second plane are located at the highest point and the lowest point of the cam, respectively.

2. The brake system of claim 1, wherein, Each hydraulic cylinder assembly includes a double-acting cylinder having a first chamber on one side of the piston and a second chamber on the other side of the piston, wherein the hydraulic circuit connects the first chamber of the first hydraulic cylinder assembly in the hydraulic cylinder assembly to the second chamber of the second hydraulic cylinder assembly in the hydraulic cylinder assembly, and connects the second chamber of the first hydraulic cylinder assembly to the first chamber of the second hydraulic cylinder assembly.

3. The brake system of claim 1, wherein, Each hydraulic cylinder assembly includes a single-acting cylinder having a first chamber defined between the cylinder and the piston, wherein the hydraulic circuit connects the first chamber of a first hydraulic cylinder assembly in the hydraulic cylinder assembly to the first chamber of a second hydraulic cylinder assembly in the hydraulic cylinder assembly.

4. The brake system according to any one of claims 1-3, wherein, The hydraulic circuit includes a four-way directional control valve system configured to ensure that the flow through the main brake valve is always in the same direction.

5. The brake system according to any one of claims 1-3, wherein, The user input device includes a brake pedal.

6. The brake system according to any one of claims 1-3, wherein, The hydraulic circuit also includes a second brake valve, which is also configured to control the flow of fluid around the hydraulic circuit, and the actuation system also includes a second user input device configured to actuate the second brake valve.

7. The braking system according to claim 6, wherein, The second user input device is a manual brake.

8. The braking system according to claim 7, wherein, Each hydraulic cylinder assembly is movable between a first position in which the cam follower is in contact with the cam and a second position in which the cam follower is out of contact with the cam, and the braking system further includes an engagement and disengagement system configured to move each hydraulic cylinder assembly between the first position and the second position.

9. The braking system according to claim 8, wherein, The engagement and disengagement system is coupled to the actuation system and configured to move each hydraulic cylinder assembly to the first position when the main brake valve is actuated, and is also configured to lock each hydraulic cylinder assembly in the first position.

10. The braking system according to claim 9, wherein, The engagement and disengagement system is also configured to move each hydraulic cylinder assembly to the first position when the second brake valve is actuated.

11. The braking system according to claim 9 or 10, wherein, The engagement and disengagement system is configured to release each hydraulic cylinder assembly from the first position when the main brake valve or the second brake valve is released, and to allow each hydraulic cylinder assembly to move to the second position.

12. The braking system according to any one of claims 8 to 10, wherein, The engagement and disengagement system includes a single-acting hydraulic cylinder connected to each hydraulic cylinder assembly and a second hydraulic circuit connected to each single-acting hydraulic cylinder, wherein hydraulic fluid is supplied to the single-acting hydraulic cylinder to move the hydraulic cylinder assembly to the first position.

13. The braking system according to claim 12, wherein, The engagement and disengagement system also includes at least one valve in the second hydraulic circuit associated with each single-acting hydraulic cylinder, wherein the at least one valve is operable to prevent hydraulic fluid from flowing out of the single-acting hydraulic cylinder in order to lock each hydraulic cylinder assembly in the first position.

14. The braking system according to any one of claims 1-3, 7-10 and 13 further includes an energy recovery system configured to transfer energy from the hydraulic fluid flowing in the hydraulic circuit to generate electricity and / or recover heat from the hydraulic fluid flowing in the hydraulic circuit.

15. The braking system of claim 14, further comprising an impeller located in the hydraulic circuit, and a power generation device operatively coupled to the impeller, which rotates the rotatable member when fluid flows through the hydraulic circuit.

16. The braking system according to claim 15, wherein, The power generation device includes an AC generator or a DC generator.

17. The braking system according to any one of claims 15-16, further comprising a heat exchanger located in the hydraulic circuit, through which the hydraulic fluid flows.

18. The braking system according to claim 17, wherein, The heat exchanger is connected to the vehicle's air conditioning system or a cooling system for goods carried by the vehicle.

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