A multi-way valve and method of operation thereof

Abstract

The application discloses a multi-way valve and a working method thereof, and relates to the technical field of multi-way valves. A first unloading valve is connected with a first flow channel, a second flow channel and a third flow channel respectively, and a second unloading valve is connected with the first flow channel, the second flow channel and the third flow channel respectively. A main action executing mechanism valve assembly is connected with the first flow channel, the second flow channel, the third flow channel and a secondary action executing mechanism valve assembly, and the main action executing mechanism valve assembly is also used for being connected with an inlet of a main action executing mechanism. The secondary action executing mechanism valve assembly is connected with the first flow channel, the second flow channel and the third flow channel respectively, and the secondary action executing mechanism valve assembly is also used for being connected with an inlet of a secondary action executing mechanism. The application can realize the confluence of hydraulic oils of a first power element and a second power element when the main action executing mechanism works, and can select the hydraulic oil of the second power element as power when the secondary action executing mechanism works.

Description

Technical Field

[0001] This invention relates to the field of multi-way valve technology, and in particular to a multi-way valve and its operating method. Background Technology

[0002] For devices with multiple actuators, the main actuator often requires a large-displacement power element to meet its operational needs, while other actuators often do not. Therefore, using a single power element to power both the main and other actuators results in wasted power and energy conservation. In practice, two power elements with different displacements are often used to power the actuators. The hydraulic fluid from both elements is combined to drive the main actuator, while one element powers the other actuators. A key challenge is figuring out how to achieve the optimal power distribution: either using the combined hydraulic fluid from two elements to power the main actuator, or using only one element to power the others. Summary of the Invention

[0003] The purpose of this invention is to provide a multi-way valve and its operating method to solve the problems existing in the prior art. It can realize the merging of hydraulic oil of the first power element and the second power element when the main actuator is working, and can select the hydraulic oil of the second power element as the power source when the auxiliary actuator is working.

[0004] To achieve the above objectives, the present invention provides the following solution: The present invention provides a multi-way valve, comprising: a first flow channel, a second flow channel, a third flow channel, a first unloading valve, a second unloading valve, a main actuator valve assembly, and a secondary actuator valve assembly; One end of the first flow channel is used to connect to the first return oil tank, and the other end of the first flow channel is used to connect to the second return oil tank; One end of the third flow channel is used to connect to the first power element, and the other end of the third flow channel is used to connect to the second power element; The first unloading valve is connected to the first flow channel, the second flow channel and the third flow channel respectively, and the second unloading valve is connected to the first flow channel, the second flow channel and the third flow channel respectively; The main actuator valve assembly is connected to the first flow channel, the second flow channel, the third flow channel, and the auxiliary actuator valve assembly, respectively. The main actuator valve assembly is also used to connect to the inlet of the main actuator. The auxiliary actuator valve assembly is connected to the first flow channel, the second flow channel and the third flow channel respectively, and the auxiliary actuator valve assembly is also used to connect to the inlet of the auxiliary actuator.

[0005] In some specific embodiments, the main actuator valve assembly includes a main valve, a main pressure compensation valve, and a directional valve. The main valve is connected to the first flow channel, the third flow channel, and the main pressure compensation valve, respectively. The main valve is also used to connect to the inlet of the main actuator. The main pressure compensation valve is connected to the second flow channel and the directional valve, respectively. The directional valve is connected to the first flow channel, the second flow channel, and the third flow channel, respectively.

[0006] In some specific designs, a main check valve is provided between the main pressure compensation valve and the main valve.

[0007] In some specific designs, a damper is provided between the main pressure compensation valve and the directional valve.

[0008] In some specific embodiments, the main actuator valve assembly further includes a pressure regulating valve, which is connected to the directional valve.

[0009] In some specific embodiments, the main actuator valve assembly further includes two secondary relief valves, both of which are connected to the first flow channel. One secondary relief valve is used to connect to the inlet of the main actuator, and the other secondary relief valve is used to connect to the outlet of the main actuator.

[0010] In some specific embodiments, the auxiliary actuator valve assembly includes an auxiliary valve and an auxiliary pressure compensation valve. The auxiliary valve is connected to the first flow channel, the third flow channel, the reversing valve, and the auxiliary pressure compensation valve, respectively. The auxiliary valve is also used to connect to the inlet of the auxiliary actuator, and the auxiliary pressure compensation valve is connected to the second flow channel.

[0011] In some specific embodiments, a steering element valve assembly and a steering signal flow channel are also included. The steering signal flow channel is connected to the second flow channel. The steering element valve assembly includes a steering priority valve, which is connected to the first flow channel, the second flow channel, and the third flow channel. The steering priority valve is also used to connect to the inlet of the steering gear.

[0012] In some specific designs, a steering check valve is provided between the steering signal channel and the second channel.

[0013] The present invention also provides a method for operating a multi-way valve, including the following operating conditions: Operating Condition 1, Standby: The hydraulic oil of the first power element enters the third flow channel, the first unloading valve opens, and the hydraulic oil of the first power element enters the first return oil tank through the first flow channel; the hydraulic oil of the second power element enters the third flow channel, the second unloading valve opens, and the hydraulic oil of the second power element enters the second return oil tank through the first flow channel. Operating Condition 2: When the main actuator is working: the hydraulic oil of the first power element and the hydraulic oil of the second power element both enter the third flow channel. The valve assembly of the main actuator is working, the second flow channel is open, the third flow channel is open, the first unloading valve and the second unloading valve are closed, and the hydraulic oil of the first power element and the hydraulic oil of the second power element merge and enter the inlet of the main actuator. Operating Condition 3: When the auxiliary actuator is working: the hydraulic oil of the second power element enters the third flow channel, the valve assembly of the auxiliary actuator is working, the second unloading valve is closed, and the hydraulic oil of the second power element enters the inlet of the auxiliary actuator; at this time, the hydraulic oil of the first power element enters the third flow channel, the first unloading valve is opened, and the hydraulic oil of the first power element enters the first return oil tank through the first flow channel.

[0014] The present invention achieves the following technical effects compared to the prior art: The multi-way valve of the present invention can combine the hydraulic oil of the first power element and the hydraulic oil of the second power element when the main actuator is working. When the auxiliary actuator is working, the hydraulic oil of the first power element and the hydraulic oil of the second power element do not combine, and only the hydraulic oil of the second power element is used to drive the auxiliary actuator, thus avoiding the waste of power. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 This is a schematic diagram of a multi-way valve in some embodiments of the present invention; In the diagram: 1-Main relief valve, 2.1-First unloading valve, 2.2-Second unloading valve, 3-First constant flow valve, 4-Secondary relief valve, 5-Main check valve, 6-Main valve, 7-Main pressure compensation valve, 8-Directional control valve, 9-Damping, 10-Survey check valve, 11-One-way throttle valve, 12-Survey priority valve, 13-LS relief valve, 14-Pressure regulating valve, 15-Auxiliary valve, 16-Auxiliary pressure compensation valve, 17-Auxiliary check valve, 18-Second constant flow valve. Detailed Implementation

[0017] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0018] The purpose of this invention is to provide a multi-way valve and its operating method to solve the problems existing in the prior art. It can realize the merging of hydraulic oil of the first power element and the second power element when the main actuator is working, and can select the hydraulic oil of the second power element as the power source when the auxiliary actuator is working.

[0019] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0020] Example 1 Taking a forklift as an example, the main actuator is the fork lifting mechanism, and there are multiple auxiliary actuators, including the fork tilting mechanism and the fork adjusting mechanism. The power of the first power element is greater than that of the second power element. The first power element is a high-flow gear pump, and the second power element is a low-flow gear pump. The fork lifting mechanism, as the main load-bearing mechanism of the forklift, is generally driven by a large-diameter hydraulic cylinder (the force of the cylinder = the pressure of the hydraulic oil × the effective area of ​​the cylinder; for the same hydraulic oil pressure, the larger the cylinder diameter, the greater the output force). Larger diameter cylinders often require a larger flow rate to meet the lifting speed requirements. The fork tilting and adjusting mechanisms are only used for fine-tuning angles and directions and generally do not require a large flow rate. The combined flow of the first and second power elements can meet the needs of the fork lifting mechanism, while the second power element can independently meet the needs of either the fork tilting or adjusting mechanism. This avoids power waste when operating the fork tilting or adjusting mechanism and allows the combined flow of the first and second power elements to meet the speed requirements of the fork lifting mechanism. At the same time, it is also necessary to consider the engine power carrying capacity under high flow output (power = pressure × flow / 600). Under high flow, the output pressure will inevitably be limited due to the limitation of engine power. The output pressure will also affect the carrying capacity of the main power actuator. It is necessary to reduce the flow under high load to achieve engine power self-adaptation. It is also necessary to provide power to the steering system and require steering priority control.

[0021] like Figure 1As shown, this embodiment provides a multi-way valve, including: a first flow channel, a second flow channel, a third flow channel, a first unloading valve 2.1, a second unloading valve 2.2, a main actuator valve assembly, and a secondary actuator valve assembly; one end (T1 port) of the first flow channel is used to connect to the first return oil tank, and the other end (T2 port) of the first flow channel is used to connect to the second return oil tank; both ends (LS1 port and LS2 port) of the second flow channel are blocked; one end (P1 port) of the third flow channel is used to connect to the first power element, and the other end (P2 port) of the third flow channel is used to connect to the second power element. The system is configured with the following components: a first unloading valve 2.1 connected to the first, second, and third flow channels, and a second unloading valve 2.2 connected to the first, second, and third flow channels; a main actuator valve assembly connected to the first, second, and third flow channels and a secondary actuator valve assembly, the main actuator valve assembly also connected to the inlet of the main actuator; and a secondary actuator valve assembly connected to the first, second, and third flow channels, the secondary actuator valve assembly also connected to the inlet of the secondary actuator. In this embodiment, the multi-way valve allows the hydraulic oil from the first power element and the second power element to merge when the main actuator is operating. When the secondary actuator is operating, the hydraulic oil from the first power element and the second power element does not merge; only the hydraulic oil from the second power element is used to drive the secondary actuator, thus avoiding power waste.

[0022] In some specific embodiments, both the first unloading valve 2.1 and the second unloading valve 2.2 are three-way unloading valves. In standby mode: the hydraulic oil of the first power element enters the third flow channel through P1, the first unloading valve 2.1 opens, and the hydraulic oil of the first power element enters the first return oil tank through the first flow channel; the hydraulic oil of the second power element enters through the third flow channel through P2, the second unloading valve 2.2 opens, and the hydraulic oil of the second power element enters the second return oil tank through the first flow channel; thus achieving the low-pressure unloading function in standby mode.

[0023] In some specific embodiments, the main actuator valve assembly includes a main valve 6, a main pressure compensation valve 7, a directional valve 8, and a pressure regulating valve 14. The main valve 6 is a three-position six-way valve, the directional valve 8 is a two-position four-way valve, and the pressure regulating valve 14 is a two-position two-way sequence valve. The main valve 6 is connected to the first flow channel, the third flow channel, and the main pressure compensation valve 7. The main valve 6 is also used to connect to the inlet of the main actuator. A main check valve 5 is provided between the main pressure compensation valve 7 and the main valve 6 to prevent oil backflow. The main pressure compensation valve 7 is connected to the second flow channel and the directional valve 8. The directional valve 8 is connected to the first flow channel, the second flow channel, and the third flow channel. The pressure regulating valve 14 is connected to the directional valve 8. A damper 9 is provided between the main pressure compensation valve 7 and the directional valve 8 to reduce the impact when the directional valve 8 switches. Furthermore, when the pressure regulating valve 14 is open, it does not affect the pressure at port P1.

[0024] The main valve 6 is equipped with pilot ports a1 and b1. When the forks are raised or lowered, the hydraulic oil of the first power element enters the third flow channel through port P1, and the hydraulic oil of the second power element enters the third flow channel through port P2. Pilot oil is passed through pilot ports a1 or b1, which pushes the main valve 6 to switch. After the hydraulic oil of the first power element enters the third flow channel through port P1, it passes through the main valve 6 and enters the main pressure compensation valve 7, which pushes the main pressure compensation valve 7 to switch. After passing through the main pressure compensation valve 7, the hydraulic oil is divided into three paths: most of the hydraulic oil passes through the main check valve 5 and the main valve 6 to the inlet A1 or B1 of the main actuator, thereby driving the main actuator to move; a small portion of the hydraulic oil passes through the damper 9 and enters the oil chamber at one end of the directional valve 8, overcoming the return spring force of the directional valve 8, thereby driving the directional valve 8 to switch, thus connecting the LS1 and LS2 ports at both ends of the second flow channel and the P1 and P2 ports at both ends of the third flow channel; another small portion of the hydraulic oil enters the second flow channel, and the hydraulic oil in the second flow channel enters the spring chamber of the first unloading valve 2.1 and the second unloading valve 2.2, thereby closing the first unloading valve 2.1 and the second unloading valve 2.2. The hydraulic oil of the first power element and the hydraulic oil of the second power element merge and pass through the inlet A1 or B1 of the main actuator to enter the cylinder of the main actuator. When operating the lifting and lowering of the forks, the merging of the hydraulic oil of the first power element and the second power element ensures that the forks are lifted and lowered quickly under low pressure.

[0025] The second flow channel is also connected in parallel with the oil chamber at one end of the pressure regulating valve 14. When the pressure in this oil chamber reaches the opening pressure controlled by the pressure regulating valve 14 through a set spring force (the spring force is adjustable), it will push the pressure regulating valve 14 to switch, connecting the oil chamber at one end of the reversing valve 8 with the first flow channel. This causes the reversing valve 8 to reset under the action of the return spring, thereby cutting off the P1 and P2 ports, and the LS1 and LS2 ports at both ends, thus achieving high-pressure non-merging. At this time, the hydraulic oil in the second flow channel no longer acts on the spring chamber of the second unloading valve 2.2, and the hydraulic oil of the second power element overcomes the return spring force of the second unloading valve 2.2, achieving low-pressure unloading. By reasonably adjusting the pressure value of the pressure regulating valve 14, it is possible to achieve self-adaptation with the engine power.

[0026] In some specific embodiments, the main actuator valve assembly further includes two secondary relief valves 4, both connected to the first flow channel. One secondary relief valve 4 is connected to the inlet of the main actuator, and the other is connected to the outlet of the main actuator. When A1 or B1 reaches the set pressure value of the corresponding secondary relief valve 4, the hydraulic oil in port A1 or B1 can open the corresponding secondary relief valve 4 to unload the load. The two secondary relief valves 4 can effectively protect the main actuator.

[0027] In some specific embodiments, the auxiliary actuator valve assembly includes an auxiliary valve 15 and an auxiliary pressure compensation valve 16. The auxiliary valve 15 is a three-position six-way valve, which is connected to the first flow channel, the third flow channel, the reversing valve 8, and the auxiliary pressure compensation valve 16. The auxiliary valve 15 is also used to connect to the inlet of the auxiliary actuator. The auxiliary pressure compensation valve 16 is connected to the second flow channel. An auxiliary check valve 17 is provided between the auxiliary pressure compensation valve 16 and the auxiliary valve 15. The auxiliary check valve 17 can prevent oil backflow.

[0028] The secondary valve 15 corresponding to the tilting mechanism is provided with pilot ports a2 and b2, the secondary valve 15 corresponding to one fork-switching mechanism is provided with pilot ports a3 and b3, and the secondary valve 15 corresponding to another fork-switching mechanism is provided with pilot ports a4 and b4. When the forks are tilted, pilot oil is supplied through pilot ports a2 or b2, which pushes the secondary valve 15 to switch. The hydraulic oil of the second power element enters the third flow channel through port P2, then passes through the secondary valve 15, and enters the secondary pressure compensation valve 16, which pushes the secondary pressure compensation valve 16 to switch. After passing through the secondary pressure compensation valve 16, the hydraulic oil is divided into two paths: most of the hydraulic oil passes through the secondary check valve 17 and the secondary valve 15 to the inlet A2 or B2 of the secondary actuator; a small portion of the hydraulic oil enters the second flow channel and enters the spring chamber of the second unloading valve 2.2, closing the second unloading valve 2.2. This allows the hydraulic oil entering from port P2 to pass through A2 or B2 and enter the cylinder of the secondary actuator that controls the fork tilting, thus completing the action. At this time, since the directional valve 8 is closed under the action of the return spring, the hydraulic oil of the first power element enters the third flow channel through port P1, overcoming the spring of the first unloading valve 2.1, and enters the first flow channel, leading to port T1, achieving low-pressure unloading, which can effectively reduce energy loss.

[0029] The fork adjustment control process is the same as the fork flipping process, so it will not be described in detail here.

[0030] In some specific embodiments, the steering element valve assembly and steering signal flow channel are also included. The steering signal flow channel is connected to the second flow channel. One end of the steering signal flow channel is a DLS port, which is used to introduce feedback signal oil to realize the LS (Load Sensing) feedback of the steering gear. The steering element valve assembly includes a steering priority valve 12, which is connected to the first flow channel, the second flow channel and the third flow channel respectively. The steering priority valve 12 is also used to connect to the inlet (D port) of the steering gear. A steering check valve 10 is provided between the steering priority valve 12 and the second flow channel. The steering check valve 10 is also connected to the steering signal flow channel. The steering check valve 10 can prevent the LS signal oil generated by other actions (operating the main action actuator and the auxiliary action actuator) from being discharged from the steering gear when the steering is not in motion.

[0031] In some specific embodiments, the steering element valve assembly further includes a one-way throttle valve 11, which is connected to the steering priority valve 12 and port D respectively. The one-way throttle valve 11 can reduce the impact during the switching process of the steering priority valve 12.

[0032] When steering is not activated, port D is essentially a closed oil chamber, and steering priority valve 12 is in the neutral position under the action of spring force. Hydraulic oil entering through port P2 of the third flow channel is directly supplied to the auxiliary actuator. When the steering gear is activated, port D is no longer a closed chamber, and the steering gear outputs feedback signal oil. The feedback signal oil enters the steering signal flow channel through port DLS and is divided into two parts: one part of the signal oil enters the second flow channel through steering check valve 10 and enters the spring chamber of the second unloading valve 2.2, thereby closing the second unloading valve 2.2, allowing the hydraulic oil entering the second power element from port P2 to act on steering priority valve 12; the other part of the signal oil acts on both ends of steering priority valve 12, pushing steering priority valve 12 to switch, so that the hydraulic oil entering the third flow channel through port P2 of the second power element passes through steering priority valve 12 and then through port D to enter the steering controller, driving the steering. When other actions and steering are operated simultaneously, steering priority valve 12 will prioritize the hydraulic oil required by the steering controller at port D, and the excess oil will enter other mechanisms.

[0033] In some specific embodiments, a main overflow valve 1 is provided between the first flow channel and the third flow channel.

[0034] In some specific embodiments, a first constant flow valve 3 and a second constant flow valve 18 are provided between the first flow channel and the second flow channel. The first constant flow valve 3 is close to the T1 port and the LS1 port, and the second constant flow valve 18 is close to the T2 port and the LS2 port. The flow rates of the first constant flow valve 3 and the second constant flow valve 18 are negligible due to the minimal change in pressure. The first constant flow valve 3 and the second constant flow valve 18 are used to ensure that the second flow channel is in dynamic equilibrium.

[0035] In some specific embodiments, an LS relief valve 13 is also included. The LS relief valve 13 is connected to the first flow channel, the second flow channel, and the second constant flow valve 18, respectively. The LS relief valve 13 is located near the T2 port and the LS2 port. When operating the fork tilting, fork adjustment control, and steering, when the hydraulic oil pressure in the second flow channel reaches the pressure value set by the LS relief valve 13, it will overcome the spring force and achieve unloading. At this time, the hydraulic oil in the spring chamber of the second unloading valve 2.2 is in an unloaded state. Under the action of the hydraulic oil at the P2 port, the second unloading valve 2.2 will open, unloading the hydraulic oil of the second power element, thereby achieving pressure protection.

[0036] The multi-way valve provided in this embodiment can meet the merging of hydraulic oil between the first and second power elements when the main actuator is working; when the auxiliary actuator is working, only the second power element is used as power, thus avoiding power waste. Simultaneously, the engine power carrying capacity under high flow output is considered; by reducing the flow rate under heavy loads, engine power self-adaptation is achieved. Furthermore, this embodiment can also achieve priority control of steering.

[0037] In this embodiment, both the main actuator valve assembly and the auxiliary actuator valve assembly are connected to the first flow channel. The two ends of the first flow channel and the two ends of the second flow channel are connected through the main actuator valve assembly. The high-flow-rate oil inlet section integrates a large-diameter first unloading valve 2.1 that ensures low-pressure unloading of the first power element during standby and can be closed during fork lifting operations, a main overflow valve 1 that limits system pressure, and a first constant flow valve 3. The reversing section controlling the main actuator integrates a high-flow-rate main valve 6 with pilot-driven reversing. The valve core of the main valve 6 is self-resetting by springs at both ends, enabling it to output a large flow rate. This section also integrates a secondary relief valve 4 to protect the main actuator, and a main pressure compensation valve 7 to ensure balanced flow distribution during compound actions. For the confluence section of the first and second power elements, this section integrates a reversing valve 8 to control the confluence switching and a pressure regulating valve 14 to control the confluence state. The reversing section controlling the auxiliary actuator integrates an auxiliary valve 15 with pilot-driven reversing, capable of controlling the flow rate according to actual demand. The valve core of the auxiliary valve 15 is self-reset by springs at both ends, and the auxiliary pressure compensation valve 16 protects the balanced distribution of flow. For the small flow oil inlet section with steering priority control, this section integrates the flow of the second power element under low pressure unloading during standby, the large-diameter second unloading valve 2.2 that can be closed when the auxiliary action actuator controls the flow and the main action actuator merges, the main relief valve 1 that limits the system pressure, the second constant flow valve 18 that unloads the second flow channel, and the steering element valve assembly that ensures steering priority. When the steering gear is operating, it can provide hydraulic oil to drive the steering, and when operating simultaneously with other actions, it can also ensure steering priority oil supply.

[0038] This embodiment provides a multi-way valve that can be used with two power components to achieve steering priority control, flow merging when the main actuator is working, and power adaptive reduction of flow output under heavy load, thus meeting the actual needs of forklift systems.

[0039] Example 2 like Figure 1 As shown, this embodiment provides a method for operating a multi-way valve according to Embodiment 1, including the following operating conditions: Operating Condition 1, Standby: The hydraulic oil of the first power element enters the third flow channel through P1, the first unloading valve 2.1 opens, and the hydraulic oil of the first power element enters the first return oil tank through the first flow channel; the hydraulic oil of the second power element enters through the third flow channel through P2, the second unloading valve 2.2 opens, and the hydraulic oil of the second power element enters the second return oil tank through the first flow channel; thus realizing the low-pressure unloading function during standby. Operating Condition 2: When the main actuator is working: the hydraulic oil of the first power element enters the third flow channel through port P1, and the hydraulic oil of the second power element enters the third flow channel through port P2. Pilot oil is supplied through pilot oil ports a1 or b1, which pushes the main valve 6 to switch. After the hydraulic oil of the first power element enters the third flow channel through port P1, it passes through the main valve 6 and enters the main pressure compensation valve 7, which pushes the main pressure compensation valve 7 to switch. After passing through the main pressure compensation valve 7, the hydraulic oil is divided into three paths: most of the hydraulic oil passes through the main check valve 5 and the main valve 6 to the inlet A1 or B1 of the main actuator, thereby driving the main actuator to move; a small portion of the hydraulic oil passes through the damper 9 and enters the oil chamber at one end of the directional valve 8, overcoming the return spring force of the directional valve 8, thereby driving the directional valve 8 to switch, thus connecting the LS1 and LS2 ports at both ends of the second flow channel and the P1 and P2 ports at both ends of the third flow channel; another small portion of the hydraulic oil enters the second flow channel, and the hydraulic oil in the second flow channel enters the spring chamber of the first unloading valve 2.1 and the second unloading valve 2.2, thereby closing the first unloading valve 2.1 and the second unloading valve 2.2. The hydraulic oil of the first power element and the hydraulic oil of the second power element merge and pass through the inlet A1 or B1 of the main actuator to enter the cylinder of the main actuator. Operating Condition 3: When the auxiliary actuator is working: Taking the fork tipping mechanism as an example, pilot oil is supplied through pilot port a1 or b1, which pushes the auxiliary valve 15 to switch. The hydraulic oil of the second power element enters the third flow channel through port P2, then passes through auxiliary valve 15 and enters the auxiliary pressure compensation valve 16, pushing the auxiliary pressure compensation valve 16 to switch. After passing through the auxiliary pressure compensation valve 16, the hydraulic oil will be divided into two paths: most of the hydraulic oil will pass through the auxiliary check valve 17 and auxiliary valve 15 to the inlet A2 or B2 of the auxiliary actuator; a small portion of the hydraulic oil will enter the second flow channel and enter the second... The spring chamber of the unloading valve 2.2 closes the second unloading valve 2.2, allowing the hydraulic oil entering through port P2 to pass through A2 or B2 and enter the cylinder of the auxiliary actuator that controls the fork tilting, thus completing the action. At this time, since the directional valve 8 is closed under the action of the return spring, the hydraulic oil of the first power element enters the third flow channel through port P1, overcomes the spring of the first unloading valve 2.1, enters the first flow channel, and leads to port T1, entering the first return oil tank to achieve low-pressure unloading, which can effectively reduce energy loss; ports LS1 and LS2 are not connected and merged. Operating Condition 4, During Steering: The feedback signal oil enters the steering signal flow channel through the DLS port and is divided into two parts: one part of the signal oil enters the second flow channel through the steering check valve 10 and enters the spring chamber of the second unloading valve 2.2, thereby closing the second unloading valve 2.2, so that the hydraulic oil entering from the P2 port of the second power element can act on the steering priority valve 12; the other part of the signal oil will act on both ends of the steering priority valve 12, pushing the steering priority valve 12 to switch, so that the hydraulic oil entering the third flow channel through the P2 port of the second power element passes through the steering priority valve 12, and then enters the steering controller through the D port to push the steering.

[0040] In the description of this invention, it should be understood that the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention. Furthermore, the terms "first," "second," "third," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Thus, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0041] In the description of this invention, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0042] If this invention discloses or relates to components or structural parts that are fixedly connected to each other, then, unless otherwise stated, a fixed connection can be understood as: a detachable fixed connection (e.g., using bolts or screws) or a non-detachable fixed connection (e.g., riveting, welding). Of course, a fixed connection can also be replaced by an integral structure (e.g., manufactured in one piece using a casting process) (except where it is obviously impossible to use an integral molding process).

[0043] In addition, unless otherwise stated, the terms used in any of the technical solutions disclosed in this invention to indicate positional relationships or shapes include states or shapes that are similar to, close to, or approximate with those states or shapes.

[0044] Any component provided by this invention can be assembled from multiple individual components or can be a single component manufactured by a one-piece molding process.

[0045] It should be noted that the structures, proportions, sizes, etc., depicted in the accompanying drawings of this specification are only used to complement the content disclosed in the specification, so as to enable those skilled in the art to understand and read them, and are not intended to limit the conditions under which the present invention can be implemented. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in the proportions, or adjustments to the size, without affecting the effects and objectives that the present invention can produce, should still fall within the scope of the technical content disclosed in the present invention.

[0046] It should also be noted that in the embodiments of this application, the same reference numerals are used to denote the same component or the same part.

[0047] Any adaptive changes made according to actual needs are within the scope of protection of this invention.

[0048] Specific examples have been used to illustrate the principles and implementation methods of this invention. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of this invention. Furthermore, those skilled in the art will recognize that, based on the ideas of this invention, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of this invention.

Claims

1. A multi-way valve, characterized in that, It includes a first flow channel, a second flow channel, a third flow channel, a first unloading valve, a second unloading valve, a main actuator valve assembly, and a secondary actuator valve assembly; One end of the first flow channel is used to connect to the first return oil tank, and the other end of the first flow channel is used to connect to the second return oil tank; One end of the third flow channel is used to connect to the first power element, and the other end of the third flow channel is used to connect to the second power element; The first unloading valve is connected to the first flow channel, the second flow channel and the third flow channel respectively, and the second unloading valve is connected to the first flow channel, the second flow channel and the third flow channel respectively; The main actuator valve assembly is connected to the first flow channel, the second flow channel, the third flow channel, and the auxiliary actuator valve assembly, respectively. The main actuator valve assembly is also used to connect to the inlet of the main actuator. The auxiliary actuator valve assembly is connected to the first flow channel, the second flow channel and the third flow channel respectively, and the auxiliary actuator valve assembly is also used to connect to the inlet of the auxiliary actuator; The main actuator valve assembly includes a main valve, a main pressure compensation valve, and a directional valve. The main valve is connected to the first flow channel, the third flow channel, and the main pressure compensation valve, respectively. The main valve is also used to connect to the inlet of the main actuator. The main pressure compensation valve is connected to the second flow channel and the directional valve, respectively. The directional valve is connected to the first flow channel, the second flow channel, and the third flow channel, respectively.

2. The multi-way valve according to claim 1, characterized in that, A main check valve is provided between the main pressure compensation valve and the main valve.

3. The multi-way valve according to claim 1, characterized in that, A damper is provided between the main pressure compensation valve and the reversing valve.

4. The multi-way valve according to claim 1, characterized in that, The main actuator valve assembly also includes a pressure regulating valve, which is connected to the directional valve.

5. The multi-way valve according to claim 1, characterized in that, The main actuator valve assembly also includes two secondary relief valves, both of which are connected to the first flow channel. One secondary relief valve is used to connect to the inlet of the main actuator, and the other secondary relief valve is used to connect to the outlet of the main actuator.

6. The multi-way valve according to claim 1, characterized in that, The auxiliary actuator valve assembly includes an auxiliary valve and an auxiliary pressure compensation valve. The auxiliary valve is connected to the first flow channel, the third flow channel, the reversing valve, and the auxiliary pressure compensation valve, respectively. The auxiliary valve is also used to connect to the inlet of the auxiliary actuator. The auxiliary pressure compensation valve is connected to the second flow channel.

7. The multi-way valve according to claim 1, characterized in that, It also includes a steering element valve assembly and a steering signal flow channel, the steering signal flow channel being connected to the second flow channel, the steering element valve assembly including a steering priority valve, the steering priority valve being connected to the first flow channel, the second flow channel and the third flow channel respectively, and the steering priority valve being used to connect to the inlet of the steering gear.

8. The multi-way valve according to claim 7, characterized in that, A one-way valve for steering is provided between the steering signal channel and the second channel.

9. A method for operating a multi-way valve as described in any one of claims 1-8, characterized in that, Including the following working conditions: Operating Condition 1, Standby: The hydraulic oil of the first power element enters the third flow channel, the first unloading valve opens, and the hydraulic oil of the first power element enters the first return oil tank through the first flow channel; the hydraulic oil of the second power element enters the third flow channel, the second unloading valve opens, and the hydraulic oil of the second power element enters the second return oil tank through the first flow channel. Operating Condition 2: When the main actuator is working: the hydraulic oil of the first power element and the hydraulic oil of the second power element both enter the third flow channel. The valve assembly of the main actuator is working, the second flow channel is open, the third flow channel is open, the first unloading valve and the second unloading valve are closed, and the hydraulic oil of the first power element and the hydraulic oil of the second power element merge and enter the inlet of the main actuator. Operating Condition 3: When the auxiliary actuator is working: the hydraulic oil of the second power element enters the third flow channel, the valve assembly of the auxiliary actuator is working, the second unloading valve is closed, and the hydraulic oil of the second power element enters the inlet of the auxiliary actuator; at this time, the hydraulic oil of the first power element enters the third flow channel, the first unloading valve is opened, and the hydraulic oil of the first power element enters the first return oil tank through the first flow channel.

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