Ride control valve

Abstract

A ride control valve includes a valve housing (30) having a main spool (32) longitudinally displaceably arranged in the valve housing, a balance spool (34), and fluid passage points for a pressure supply (P), a tank return line (T), an accumulator (14) and a boom cylinder unit (10). The balance spool (34) continuously balances the pressure between the fluid ports of the accumulator (14) and the boom cylinder unit (10). The main spool (32) is controlled by the operator and initially interconnects these fluid ports of the accumulator (14) and the boom cylinder unit (10), starting from a closed fluid connection, via a restricted fluid connection, to a fully opened fluid connection, or disconnects them from each other in reverse sequence.

Claims

1. A ride control valve, comprising: a valve housing having a pressure supply port, a tank line port, an accumulator port and a boom cylinder unit port; a main spool longitudinally displaceable in the valve housing, controllable by an operator and initially interconnecting the accumulator port and the boom cylinder unit port in fluid communication from a closed fluid connection via a restricted fluid connection and then to a fully opened fluid connection or disconnecting the interconnecting of the accumulator port and the boom cylinder unit port from fluid communication from the fully opened fluid connection and then to the closed fluid connection via the restricted fluid connection, the main spool including a longitudinal channel having a first axial end opening into a control chamber having a spring therein biasing the main spool to an initial center position thereof and a second axial end opening into a restriction and including a transverse connection with a larger cross-sectional area than the restriction located on a side of the restriction remote from the first axial end opening into the tank line port; and a balance spool longitudinally displaceable in the valve housing, continuously balancing fluid pressure between the accumulator port and the boom cylinder unit port.

2. A ride control valve according to claim 1 wherein the balance spool is accommodated in a balance spool chamber in the valve housing, is spring biased in an initial center position thereof, and is subjected to fluid pressure from the accumulator port at a first axial end of the balance spool and subjected to fluid pressure from the boom cylinder unit port at a second axial end of the balance spool; whereby to achieve a continuous pressure balance between the accumulator port and the boom cylinder unit port, the balance spool is movable in a first axial direction connecting the accumulator port and the pressure supply port in fluid communication when pressure at the boom cylinder unit port is greater than pressure at the accumulator port, and the balance spool is movable in an opposite second axial direction connecting the accumulator port and the tank line port in fluid communication when the pressure at the accumulator port is greater than the pressure at the boom cylinder unit port.

3. A ride control valve according to claim 1 wherein the main spool is accommodated in a main spool chamber in the valve housing and is movable by a pilot valve actuatable by the operator and supplying fluid pressure against a spring biasing force on the main spool to a position establishing the fully opened position providing fluid communication between the accumulator port and the boom cylinder unit port.

4. A ride control valve according to claim 3 wherein the main spool comprises a pilot restriction on an outer circumference thereof connecting pilot pressure from the pilot valve into a control chamber in the main spool chamber receiving the main spool, the main spool being movable by the pilot pressure toward the fully opened fluid connection from the initial center position thereof when the spring biasing force is exceeded, with a fluid connection between the pilot valve and the control chamber being increasingly interrupted by the pilot restriction.

5. A ride control valve according to claim 4 wherein the pilot restriction comprises a transverse drilled hole in the main spool extending into a longitudinal drilled hole in the main spool opening into the control chamber.

6. A ride control valve according to claim 3 wherein the pilot valve is inserted in the valve housing and is actuatable by an actuating solenoid, energization of the actuating solenoid being operator-controlled.

7. A ride control valve according to claim 3 wherein the pilot control valve is connected in fluid communication with a pilot pressure control port independent of the pressure supply port, pressure at the pilot pressure control port being lower than pressure at the pressure supply port.

8. A ride control valve according to claim 1 wherein a cross section of the main spool is reduced in an area of the boom cylinder unit port in a direction of the accumulator port forming a restriction and establishing a restricted fluid connection between the accumulator port and the boom cylinder unit port.

9. A ride control device, comprising: a hydraulic boom cylinder unit; a hydraulic accumulator; a ride control valve having a main spool and a balance spool in a valve housing connecting the hydraulic boom cylinder unit and the hydraulic accumulator, the valve housing including a pressure supply port connected to a pump in fluid communication, a tank line port connected in fluid communication to a tank, an accumulator port connected in fluid communication with the hydraulic accumulator, and a boom cylinder unit port connected in fluid communication with the hydraulic boom cylinder unit; and a pilot valve connected in the valve housing at least partially controlling movement of the main spool in the valve housing, the main spool being longitudinally displaceable in the valve housing, being controllable by an operator by the pilot valve and initially interconnecting the accumulator port and the boom cylinder unit port in fluid communication from a closed fluid connection via a restricted fluid connection and then to a fully opened fluid connection or disconnecting the interconnecting of the accumulator port and the boom cylinder unit port from fluid communication from the fully opened fluid connection and then to the closed fluid connection via the restricted fluid connection, the balance spool being longitudinally displaceable in the valve housing and continuously balancing fluid pressure between the accumulator port and the boom cylinder unit port, the main spool including a longitudinal channel having a first axial end opening into a control chamber having a spring therein biasing the main spool to an initial center position thereof and a second axial end opening into a restriction and including a transverse connection with a larger cross-sectional area than the restriction located on a side of the restriction remote from the first axial end opening into the tank line port.

10. A ride control device according to claim 9 wherein the balance spool is accommodated in a balance spool chamber in the valve housing is spring biased in an initial center position thereof, and is subjected to fluid pressure from the accumulator port at a first axial end of the balance spool and subjected to fluid pressure from the boom cylinder unit port at a second axial end of the balance spool; whereby to achieve a continuous pressure balance between the accumulator port and the boom cylinder unit port, the balance spool is movable in a first axial direction connecting the accumulator port and the pressure supply port in fluid communication when pressure at the boom cylinder unit port is greater than pressure at the accumulator port, and the balance spool is movable in an opposite second axial direction connecting the accumulator port and the tank line port in fluid communication when the pressure at the accumulator port is greater than the pressure at the boom cylinder unit port.

11. A ride control device according to claim 9 wherein the main spool is accommodated in a main spool chamber the valve housing and is movable by the pilot valve actuatable by the operator and supplying fluid pressure against a spring biasing force on the main spool to a position establishing the fully opened position providing fluid communication between the accumulator port and the boom cylinder unit port.

12. A ride control device according to claim 11 wherein the main spool comprises a pilot restriction on an outer circumference thereof connecting pilot pressure from the pilot valve into a control chamber in the main spool chamber receiving the main spool, the main spool being movable by the pilot pressure toward the fully opened fluid connection from the initial center position thereof when the spring biasing force is exceeded, with a fluid connection between the pilot valve and the control chamber being increasingly interrupted by the pilot restriction.

13. A ride control device according to claim 12 wherein the pilot restriction comprises a transverse drilled hole in the main spool extending into a longitudinal drilled hole in the main spool opening into the control chamber.

14. A ride control device according to claim 11 wherein the pilot valve is inserted in the valve housing and is actuatable by an actuating solenoid, energization of the actuating solenoid being operator-controlled.

15. A ride control device according to claim 11 wherein the pilot control valve is connected in fluid communication with a pilot pressure control port independent of the pressure supply port, pressure at the pilot pressure control port being lower than pressure at the pressure supply port.

16. A ride control device according to claim 9 wherein a cross section of the main spool is reduced in an area of the boom cylinder unit port in a direction of the accumulator port forming a restriction and establishing a restricted fluid connection between the accumulator port and the boom cylinder unit port.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Referring to the drawings that form a part of this disclosure and that are general and not to scale:

(2) FIG. 1 is a schematic hydraulic circuit diagram of the basic structure of a ride control valve according to a first exemplary embodiment of the invention;

(3) FIG. 2 is a side view in section of the main components of the ride control valve shown in the schematic diagram in FIG. 1;

(4) FIGS. 3-5 are partial side views in section of the ride control valve according to FIG. 2 showing the main spool in different displacement positions; and

(5) FIG. 6 is a partial side view in section of a ride control valve with a modified main spool according to a second exemplary embodiment of the invention.

DETAILED DESCRIPTION OF THE INVENTION

(6) The hydraulic circuit diagram according to FIG. 1 shows a hydraulic boom cylinder unit 10 having a single piston cylinder 12. Instead of a single boom cylinder 12. Several such boom cylinders, in particular two boom cylinders, can be interconnected to form the cylinder unit 10, for instance to move the loading bucket of a mobile machine, for instance in the form of a wheel loader (not shown). Depending on the load in the loading bucket, different load conditions occur, in particular in the front wheel area of the wheel loader. To cushion the boom cylinder unit 10, in particular when the mobile machine is driven or to dampen its possible travel motions, a hydraulic accumulator 14 is provided, which can be made up of one or more hydraulic accumulators of conventional design, for instance in the form of piston accumulators, bladder accumulators, diaphragm accumulators, etc. The hydraulic accumulator 14 is connected to a hydraulic fluid circuit 16 as shown in FIG. 1. The fluid of the hydraulic fluid circuit 16, typically a hydraulic fluid, can be rest inside the accumulator 14 against a gas supply thereof in the usual manner and typically subject to a preload.

(7) The hydraulic fluid circuit 16 is supplied with fluid of predeterminable pressure and quantity by a pressure supply device 18, typically in the form of a hydraulic pump, from a supply tank 20. A check valve 22, which closes in the direction of the pressure supply device 18 and opens in the opposite direction is provided to prevent any unintentional backflow of fluid in the direction of the hydraulic pump 18. Furthermore, as part of a closed loop system, excess fluid from the fluid circuit 16 is recirculated to the supply tank 20 for re-withdrawal using the hydraulic pump 18. The boom cylinder 12 shown in FIG. 1 is designed as a differential cylinder and has a piston or base end 24, which is separated from a rod chamber 28 by a longitudinally movable piston-rod-unit 26. Both the piston end 24 and the rod end 28 are enclosed by a cylinder housing in the usual manner. Both the piston end 24 and the rod end 28 are connected to the fluid circuit 16 in a fluid-conveying manner.

(8) The valve device or ride control valve for controlling the transfer of fluid between the boom cylinder unit 10 and the accumulator 14 is installed between the two fluid components, as shown in FIG. 1. For an actuation, the valve device has a main spool 32 longitudinally displaceably arranged in a valve housing 30 (FIG. 2), in addition to a balance spool 34 and a pilot valve 36, which can be actuated by an operator of the mobile machine and which can be actuated by an actuating solenoid device 38.

(9) The balance spool 34 is spring-centered between two compression springs 40 of the same design and held in its initial position shown in FIG. 1, in which the fluid ports for the pressure supply P and for the tank return line T are separated from each other and from an outlet A leading in the direction of the accumulator 14. Furthermore, the balance spool 34 interacts with two orifices 42 and 44 in an assigned hydraulic control line, which orifices are preferably of the same design. If the fluid pressure increases in the boom cylinder unit 10 on the piston end or base end 24, for instance because the piston rod unit 26 moves into the housing of the boom cylinder due to force, the balance spool 34 is moved to the left into its right actuating position, as viewed in the direction of FIG. 1, provided the accumulator pressure of the accumulator 14 is lower than the spool pressure on the piston end or base end 24. In this case, when the hydraulic pump 18 is switched on, fluid is supplied to the outlet end A via the pressure supply port P. When the main spool 32 is in the switching position or actuating position shown in FIG. 1, fluid at a presettable pressure level enters the accumulator 14 until pressure balance is again achieved at the two opposite ends of the balance spool 34, with the result that the balance spool 34 returns to its initial or blocking position shown in FIG. 1.

(10) If the fluid pressure on the end of the accumulator 14 is greater than on the bottom end 24 of the boom cylinder unit 10, the balance spool 34 moves to the right into its left switching or actuating position, in which the accumulator 14 discharges fluid via port A in the direction of the tank return line T, and thus, discharges to the supply tank 20 without pressure. This process continues until a pressure equilibrium is again achieved at the opposite control ends of the equalizing spool 34. The prerequisite for the pressure adjustment is again the main spool 32 moving to its switching position shown in FIG. 1. The main task of the balance spool 34 is then to keep the relevant fluid pressures both on the end of the boom cylinder unit 10 and on the end of the accumulator 14 constantly at the same level during normal working mode of the mobile machine, for instance in the context of picking up or setting down a load as part of the bucket operation, to enable jolt-free and low-vibration switching on of the damping device as soon as the mobile machine moves in drive mode from a location A to a location B, irrespective of the load situation at the bucket and consequently at the boom cylinder unit 10. Insofar as, as in this exemplary embodiment, the boom cylinder unit 10 is directly assigned to the actuation of the excavator or loading bucket, this is not mandatory and the boom cylinder unit 10 can also be used to support other load-dependent components that are present in the area of a mobile machine.

(11) If the pilot valve 36 is actuated by the actuating solenoid device 38, it moves to its upper switching position as viewed in the direction of FIG. 1. An independent pressure supply device (not shown) is used to apply a fluid pressure P′, which is reduced in comparison to the pressure P of the hydraulic pump 18. Fluid pressure P′ is supplied to the right-hand hydraulic control end of the main spool 32 after passing through a restriction or further orifice 46 in the main spool 32. As the fluid pressure increases, the main spool 32 is moved to the left into its right-hand actuating or travel position against the action of a further compression spring 48. Fluid then increasingly reaches the right-hand control end of the spool 32 via the restriction 46 and its increasing opening cross-section. In this way, a fluid connection from the accumulator 14 to the piston end or base end 24 of the boom cylinder unit 10 is gradually established, whereas the rod chamber 28 is de-pressurized in the direction of the supply tank 20 and, if necessary, excess fluid reaches the fluid supply tank 20 via the open-centered main spool 32. While initially this fluid connection between the accumulator 14 and the boom cylinder unit 10 is established in a restricted manner, ultimately the cross-section of the main spool 32 opens fully, and the boom cylinder unit 10 can be supported as a whole by the accumulator 14 in damping mode when the mobile machine is driven. This arrangement is extremely comfortable for the operator of such a machine, because a low-vibration operation is achieved without jolting. Any motion shocks during drive operation are safely absorbed by the accumulator 14 by the main spool 32 with the valve device in the fully open position.

(12) When the driving operation is finished and the working mode using the loading bucket is resumed, the pilot valve 36 is returned to its unactuated position as shown in FIG. 1. The consequence is that the hydraulic control pressure at the main spool 32 is depressurized via the tank return line T′. The partial spring centering by the further pressure spring 48 of the main spool 32 is used to move it to its position shown in FIG. 1, which is equivalent to switching off the damping device by the accumulator 14. The balancing processes described above between the operating pressures of the accumulator 14 and the boom cylinder unit 10 again occur via the balance spool 34.

(13) Below, the valve device according to the invention as used in the ride control device according to FIG. 1 is described in more detail with reference to FIG. 2. Thus, the valve device according to the embodiment shown in FIG. 2 has a one-piece valve housing 30. However, it is understood that a valve housing to this effect may also be of multi-part design. Fluid ports are provided for the pressure supply P and the tank return line T on the bottom end of the valve housing 30. The longitudinally movable balance spool 34 is arranged superjacent thereof, which is shown spring-centered via the two compression springs 40 in its locking central or initial position. On both opposite ends of the balance spool 34, two longitudinal drilled holes of equal length are made, each having the orifice 42 or 44 on its free end face. At their ends facing each other, the two longitudinal channels open into one transverse channel 50 each. One of the transverse channels 50 opens into a fluid chamber 52, in which the fluid connection pressurizes the fluid at the piston end or base end 24 of the boom cylinder unit 10. The other transverse channel 50 opens into another fluid chamber 54, which leads to a fluid port S to which the accumulator 14 is connected.

(14) Furthermore, longitudinal grooves are introduced in the outer circumference of the balance spool 34. The central longitudinal groove marked “A” establishes a fluid connection between the pressure supply port P and the accumulator port S via the blind channel 56 when the balance spool 34 is displaced to the far left as viewed in the direction of FIG. 2. In the opposite direction of displacement of the balance spool 34 to the right, in the shown position of the main spool 32, the fluid pressure from the end of the accumulator 14 reaches the tank return end T via the accumulator connection S and the central, vertically extending blind line 58 and the further fluid connection 60 in the manner of a blind line. For a displacement motion of the balance spool 34 to the left, the pressure in the control chamber 62 is higher than on the opposite end having the further control chamber 64. The control chamber 62 is pressurized via the fluid chamber 52, the transverse channel 50 and the restriction 42. If the pressure in the further control chamber 64 is higher than the pressure in control chamber 62, the balance spool 34 is moved to the right. The pressure in the further control chamber 64 builds up from the end of the accumulator connection S via the assigned transverse channel 50 and longitudinal drilled hole with adjoining further restriction 44. When the balance spool 34 is moved to the left, the pressure at the accumulator port S is increased by connecting this accumulator port S to the pressure supply port P. When the balance spool 34 moves to the right, on the other hand, which happens when the pressure at the accumulator port S is greater than the pressure of the boom cylinder unit 10 in the fluid chamber 52, a fluid connection is established between the accumulator port S and the tank return port T until once again, there is a pressure equilibrium between the accumulator 14 and the boom cylinder unit 10, resulting in the balance spool 34 resuming its spring-centered initial position shown in FIG. 2.

(15) Viewed in the direction of FIG. 2, the main spool 32 is arranged above the balance spool 34. Both spools 32, 34 are guided longitudinally movable in parallel to each other in the valve housing 30. The various embodiments and possible travel positions of the main spool 32 are shown in more detail in FIGS. 3-6, i.e. further reference will be made to these below. The left end of the main spool 32 rests in a partially centered manner against the further compression spring 48, as explained above. In its initial position shown in FIG. 2, the main spool 32 covers a further fluid chamber 66, which, as in the fluid chamber 52, is pressurized by the spool end or base end 24 of the boom cylinder unit 10. The fluid routing is shown in the hydraulic circuit diagram in FIG. 1. Furthermore, the main spool 32 has, opposite from the accumulator port S, a bore 68, which transitions at the edge into control edges 70. Control edges 70 are designed as a restriction and are part of a ledge. The ledge transitions into the larger outer diameter of the outer circumference of the main spool 32 and, opposite the control edges 70, into a smaller diameter formed by the bore 68 in the main spool 32. Viewed in the direction of FIG. 2, the main spool 32 covers a vertically extending fluid duct 72, which opens at one end at the tank return line T and is closed by a plug 74 at the other, opposite end as the additional return port T′ in the valve housing 30. The plug is removed to establish the tank return connection at start-up. Furthermore, the actuating solenoid device 38 of the pilot valve 36 extends through the valve housing 30 from above, together with the associated fluid duct 72. The solenoid free actuating end face is inserted in the valve housing 30, for instance screwed in or secured to the top of the valve housing 30 by a flange plate. On the upper end of the pilot valve 36, there is a connector 76 for connecting an electrical connection to the actuating solenoid device 38 of the pilot valve 36. The solenoid device is energized by an operator of the mobile machine to establish the mentioned damping connection, which actuates the pilot valve 36.

(16) In a further sequence, the main spool 32 having a stepped diameter reduction passes through a further fluid chamber 78, which is connected to the rod end or rod chamber 28 of the boom cylinder unit 10 in a fluid-conveying manner. On its bottom end, the pilot valve 36 opens into a connecting channel 80 that, according to the illustration of FIG. 2, is traversed by the main spool 32 from the further or pilot restriction 46. Restriction 46 is arranged between a transverse channel and a longitudinal channel in the main spool 32. The longitudinal channel opens into a further control chamber 84, such that, when a corresponding pressure builds up in the further control chamber 84, the main spool 32 moves from its initial position to the left, as viewed in the direction of FIG. 2, against the action of the further compression spring 48. During the displacement motion of the main spool 32 in this left direction, it travels to the respective positions as shown in FIGS. 3-5, which are explained in more detail below.

(17) The operator decides when to engage the ride control system. This occurs when the operator energizes the main ride control solenoid 38 of the pilot valve 36. When this happens, pilot pressure is applied to the right of the main spool 32 in the chamber 84 via the orifice 46.

(18) As shown in FIG. 3, the orifice 46 restricts the amount of flow that can enter the control chamber 84. All the flow through the pilot valve 36 must pass through the orifice 46 because of the spool overlap condition 86. This overlap condition causes the main spool 32 to slowly shift to the left. As the main spool 32 slowly shifts to the left, the left side notch 70 opens and the fluid flows into chamber 66 regulating the flow from the base end 24 of the cylinder unit 10 to the accumulator 14. In this way, the pressures are balanced in a controlled manner that can be adapted to the customer's needs.

(19) As shown in FIG. 4, when the main spool 32 continues to shift to the left the spool overlap condition 86 becomes zero. When this happens, the spool orifice 46 is bypassed, and the pressure regulated by the pilot valve 36 is directly applied to the chamber 84. When this happens, the spool 32 rapidly moves further to the left and quickly shifts to the wide-open position. This movement also ends any soft-shift regulation from the left side notch 70 in the main spool 32.

(20) As shown in FIG. 5, when the main spool 32 is in the fully extended position, there is a new connection 88 that is open between the connection line 80 controlled by the pilot valve 36 and the hydraulic chamber 84. This opening provides a very easy path to go from fluid line 80 to chamber 84 with very little restriction. When the main spool 32 is in the fully extended position it also makes for very little resistance between the base end 24 of the cylinder unit 10 and the accumulator 14. This connection allows all pressure loads to pass through these points with very little restriction, resulting in a softer ride for the operator of the mobile machine, and a full dampening effect was reached for the hydraulic boom unit 10.

(21) The solution according to FIG. 6 shows an alternative embodiment to the valve solutions above. In this solution, the main spool 32 has a longitudinal channel 94, one end of which opens into a further control chamber 96 with partial spring centering. The other free end region of channel 94 opens into a further, fourth restriction 98. After this restriction 98 is passed, with increasing overlap, a subsequent transverse connection 100 having a comparatively larger cross-sectional area opens into the tank return line T.

(22) This alternate embodiment of the configuration according to the invention shows how the same soft-shift effect can be obtained on the opposite end of the main spool 32. As the pilot pressure is increased in the chamber 84, the main spool 32 is moved towards the open position. However, this motion is resisted because of the fluid trapped in the spring chamber 96. The fluid in the chamber 96 has to pass through the channel 94 and then across the orifice 98 much in the same way as it does across the orifice 46 according to the first solution described above. The fluid slowly passes through the orifice 98 and is drained to the tank line T. This slow drainage allows the main spool 32 to slowly move towards the open position until the point in time the channel 100 opens into the tank line chamber having the tank connection T. At this time, the fluid can bypass the orifice 98 and will immediately enter the chamber T. This bypassing allows the main spool 32 to quickly move into the open position to guarantee the full dampening effect for the hydraulic boom cylinder unit 10 by the accumulator or dampening device 14.

(23) Summarized, this invention can be used to let the main spool 32 slowly shift to a narrowed open position in the first part of the spool stroke and then to quickly shift to the completely open position once the main spool 32 has reached a certain position. In this way, the pressure can be slowly balanced between the base end 24 of the cylinder unit 10 and the accumulator 14 via at least one notch 70 in the spool stroke for a certain period of time and then be fully opened to allow for maximum flow between the base end 24 of the cylinder unit 10 and the accumulator 14, which significantly reduces vibrations and increases the operator's comfort.

(24) While various embodiments have been chosen to illustrate the invention, it will be understood by those skilled in the art that various changes and modifications can be made therein without departing from the scope of the invention as defined in the claims.