Control valve, fluid system, construction machine, and actuator drive control method

Abstract

The present application provides a control valve, a fluid system, a construction machine, and an actuator drive control method. The independent metering valve (2) of the embodiment is provided with a first inlet throttle valve column (5), a second inlet throttle valve column (6), and a bridge flow path (30). The first inlet throttle valve column (5) has a first inlet throttle flow path (11) that communicates with a first pump (110A). The second inlet throttle valve column (6) has a second inlet throttle flow path (12) that communicates with a second pump (110B). The bridge flow path (30) communicates with the first inlet throttle flow path (11) and the second inlet throttle flow path (12), and communicates with each port (Hp, Rp) of a hydraulic actuator (111).

Description

Technical Field

[0001] This invention relates to a control valve, a fluid system, construction machinery, and an actuator drive control method. Background Technology

[0002] Construction machinery, such as hydraulic excavators, is driven by various actuators. These actuators are driven by working oil (fluid) ejected from a pump (hydraulic pump). The actuator's drive is controlled by a fluid system that adjusts the flow rate of the working oil. This fluid system includes, for example, a control valve equipped with a valve stem. By moving the valve stem, the control valve can adjust the width (shape) of the flow path through which the working oil flows. This allows for adjustment of the flow rate of the working oil supplied to the actuator.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 6-193604 Summary of the Invention

[0006] The problem the invention aims to solve

[0007] However, in the aforementioned existing control valves and fluid systems, there is a possibility that it is difficult to adjust the flow rate of the working oil supplied to the actuator with high performance to cope with the operation of construction machinery.

[0008] This invention provides a control valve, a fluid system, construction machinery, and an actuator drive control method capable of high-performance adjustment of the flow rate of fluid supplied to an actuator.

[0009] Solution for solving the problem

[0010] (1) One aspect of the control valve of the present invention comprises: a first inlet throttling valve column having a first inlet throttling flow path communicating with a first pump; a second inlet throttling valve column having a second inlet throttling flow path communicating with a second pump; and a supply flow path communicating with the first inlet throttling flow path and the second inlet throttling flow path, and communicating with the supply and discharge ports of an actuator.

[0011] With this configuration, the first inlet throttling valve is driven and controlled to connect the first inlet throttling flow path to the first pump. Similarly, the second inlet throttling valve is driven and controlled to connect the second inlet throttling flow path to the second pump. Thus, for example, by adjusting the flow rate of fluid ejected from the first pump to 100% and the flow rate of fluid ejected from the second pump to 0% to 100%, it is possible to merge the fluids ejected from at least one of the first and second pumps in the supply flow path.

[0012] As a result, the ratio of fluid supplied to the actuator from the first and second pumps can be arbitrarily (freely) changed within a range of twice the ejection volume of each pump. Therefore, the flow rate of the fluid supplied to the actuator can be adjusted with high performance.

[0013] (2) In the above structure, the control valve may also have an inlet throttle valve receiving part that houses the first inlet throttle valve and the second inlet throttle valve together.

[0014] (3) In the above structure, the inlet throttle valve column receiving part may also have a middle part, which is located in the middle of the first inlet throttle valve column and the second inlet throttle valve column in the axial direction of each inlet throttle valve column, and communicates with the tank.

[0015] (4) In the above structure, the control valve may also have an outlet throttle valve column, which has a flow path connected to the supply flow path and the supply and discharge port of the actuator.

[0016] (5) In the above structure, the first inlet throttle valve column may also have a recess that connects the supply flow path to the supply and discharge port of the actuator, or connects the supply and discharge port of the actuator to the tank.

[0017] (6) In the above structure, the second inlet throttle valve column may also have another recess that connects the supply flow path to the supply and discharge port of the actuator, or connects the supply and discharge port of the actuator to the tank.

[0018] (7) In the above structure, the control valve may also have a module body that includes the first inlet throttle valve column, the second inlet throttle valve column, and the outlet throttle valve column.

[0019] (8) Another aspect of the control valve of the present invention comprises: a first inlet throttling valve column having a first inlet throttling flow path communicating with a first pump; a second inlet throttling valve column having a second inlet throttling flow path communicating with a second pump; a supply flow path communicating with the first inlet throttling flow path and the second inlet throttling flow path, and communicating with the supply and discharge ports of an actuator; an outlet throttling valve column having a flow path communicating with the supply flow path and the supply and discharge ports of the actuator; a module body having the first inlet throttling valve column, the second inlet throttling valve column, and the outlet throttling valve column disposed thereon; and an inlet throttling valve column receiving portion disposed in the module body, having received the first inlet throttling valve column and the second inlet throttling valve column. The inlet throttling valve column receiving portion has a middle portion disposed at the midpoint between the first inlet throttling valve column and the second inlet throttling valve column in the axial direction of each inlet throttling valve column, and communicating with a tank.

[0020] With this configuration, the first inlet throttling valve is driven and controlled to connect the first inlet throttling flow path to the first pump. Similarly, the second inlet throttling valve is driven and controlled to connect the second inlet throttling flow path to the second pump. Thus, for example, by adjusting the flow rate of fluid ejected from the first pump from 0 to 100%, and by adjusting the flow rate of fluid ejected from the second pump from 0 to 100%, it is possible to merge the fluids ejected from at least one of the first and second pumps in the supply flow path.

[0021] As a result, the ratio of fluid supplied to the actuator from the first and second pumps can be arbitrarily (freely) changed within a range of twice the ejection volume of each pump. Therefore, the flow rate of the fluid supplied to the actuator can be adjusted with high performance.

[0022] Furthermore, the flow path of the outlet throttle valve is connected to the supply flow path, and the flow path of the outlet throttle valve is also connected to the supply and discharge ports of the actuator. The first inlet throttling flow path of the first inlet throttle valve and the second inlet throttling flow path of the second inlet throttle valve are connected to the supply flow path. Therefore, the outlet throttle valve can be universally used for both the first and second inlet throttle valves. Consequently, the number of outlet throttle valves can be reduced to one, simplifying the structure of the control valve.

[0023] Furthermore, the first inlet throttle valve, the second inlet throttle valve, and the outlet throttle valve are all housed within the module. This reduces the number of modules and simplifies the control valve design, resulting in a more compact configuration.

[0024] Furthermore, both the first and second inlet throttle valve stems are housed together in the inlet throttle valve stem housing. This reduces the number of inlet throttle valve stem housings and simplifies the control valve structure.

[0025] Furthermore, an intermediate section is formed between the first and second inlet throttle valve columns in the inlet throttle valve column housing, axially opposite each other. This intermediate section connects the tank to the tank. Therefore, if the first and second inlet throttle valve columns move, for example, by reducing the volume of the intermediate section, the fluid in the intermediate section can be discharged into the tank. As a result, it is possible to prevent the pressure of the fluid in the intermediate section from increasing, thus preventing the inlet throttle valve columns from becoming difficult to move. Consequently, the first and second inlet throttle valve columns can move smoothly within the inlet throttle valve column housing.

[0026] (9) Another aspect of the control valve of the present invention comprises: a first inlet throttling valve column having a first inlet throttling flow path communicating with a first pump; a second inlet throttling valve column having a second inlet throttling flow path communicating with a second pump; a supply flow path communicating with the first inlet throttling flow path and the second inlet throttling flow path, and communicating with the supply and discharge ports of an actuator; an outlet throttling valve column having a flow path communicating with the supply flow path and the supply and discharge ports of the actuator; a module body having the first inlet throttling valve column, the second inlet throttling valve column, and the outlet throttling valve column disposed thereon; and an inlet throttling valve column receiving portion disposed thereon in the module body, having received the first inlet throttling valve column and the second inlet throttling valve column together. The inlet throttle valve column receiving portion has a middle portion, which is disposed in the middle of the first inlet throttle valve column and the second inlet throttle valve column in the axial direction of each inlet throttle valve column, and communicates with the tank. The first inlet throttle valve column has a recess that connects the supply flow path to the supply and discharge port of the actuator, or connects the supply and discharge port of the actuator to the tank. The second inlet throttle valve column has another recess that connects the supply flow path to the supply and discharge port of the actuator, or connects the supply and discharge port of the actuator to the tank.

[0027] With this configuration, the first inlet throttling valve is driven and controlled to connect the first inlet throttling flow path to the first pump. Similarly, the second inlet throttling valve is driven and controlled to connect the second inlet throttling flow path to the second pump. Thus, for example, by adjusting the flow rate of fluid ejected from the first pump from 0 to 100%, and by adjusting the flow rate of fluid ejected from the second pump from 0 to 100%, it is possible to merge the fluids ejected from at least one of the first and second pumps in the supply flow path.

[0028] As a result, the ratio of fluid supplied to the actuator from the first and second pumps can be arbitrarily (freely) changed within a range of twice the ejection volume of each pump. Therefore, the flow rate of the fluid supplied to the actuator can be adjusted with high performance.

[0029] Furthermore, the flow path of the outlet throttle valve is connected to the supply flow path, and the flow path of the outlet throttle valve is also connected to the supply and discharge ports of the actuator. The first inlet throttling flow path of the first inlet throttle valve and the second inlet throttling flow path of the second inlet throttle valve are connected to the supply flow path. Therefore, the outlet throttle valve can be universally used for both the first and second inlet throttle valves. Consequently, the number of outlet throttle valves can be reduced to one, simplifying the structure of the control valve.

[0030] Furthermore, the first inlet throttle valve, the second inlet throttle valve, and the outlet throttle valve are all housed within the module. This reduces the number of modules and simplifies the control valve design, resulting in a more compact configuration.

[0031] Furthermore, both the first and second inlet throttle valve stems are housed together in the inlet throttle valve stem housing. This reduces the number of inlet throttle valve stem housings and simplifies the control valve structure.

[0032] Furthermore, an intermediate section is formed between the first and second inlet throttle valve columns in the inlet throttle valve column housing, axially opposite each other. This intermediate section connects the tank to the tank. Therefore, if the first and second inlet throttle valve columns move, for example, by reducing the volume of the intermediate section, the fluid in the intermediate section can be discharged into the tank. As a result, it is possible to prevent the pressure of the fluid in the intermediate section from increasing, thus preventing the inlet throttle valve columns from becoming difficult to move. Consequently, the first and second inlet throttle valve columns can move smoothly within the inlet throttle valve column housing.

[0033] Furthermore, the first inlet throttle valve column has a recess positioned between the supply flow path and the actuator's supply / discharge ports. Therefore, the supply flow path can be connected to the actuator's supply / discharge ports via the recess. Consequently, the pressure loss of the fluid supplied from the supply flow path to the actuator can be reduced.

[0034] Furthermore, the recess is positioned between the actuator's supply and discharge ports and the tank. Therefore, the actuator can communicate with the tank via the recess. Consequently, the flow rate of fluid returning from the actuator to the tank can be increased.

[0035] Furthermore, the second inlet throttle valve column has another recess, positioned between the actuator's supply and discharge ports and the tank. This allows the actuator to communicate with the tank via the other recess, thereby increasing the flow rate of fluid returning from the actuator to the tank.

[0036] Furthermore, another recess is positioned between the supply flow path and the supply / discharge port of the actuator. Therefore, the supply flow path can be connected to the actuator via this other recess. Consequently, the pressure loss of the fluid supplied from the supply flow path to the actuator can be reduced.

[0037] (10) Another aspect of the fluid system of the present invention comprises: a first pump and a second pump; an actuator driven by fluid ejected from the first pump and the second pump; and a control valve disposed between the first pump and the second pump and the actuator, for adjusting the flow rate of the fluid supplied to the actuator or the flow rate of the fluid discharged from the actuator. The control valve comprises: a first inlet throttling valve column having a first inlet throttling flow path communicating with the first pump; a second inlet throttling valve column having a second inlet throttling flow path communicating with the second pump; a supply flow path communicating with the first inlet throttling flow path and the second inlet throttling flow path, and communicating with the supply and discharge ports of the actuator; and an outlet throttling valve column having a flow path communicating with the supply flow path and the supply and discharge ports of the actuator.

[0038] By configuring the fluid system in such a way that the first inlet throttling valve is driven and controlled to connect the first inlet throttling flow path to the first pump, and the second inlet throttling valve is driven and controlled to connect the second inlet throttling flow path to the second pump, the fluid ejected from the first pump and the fluid ejected from the second pump can be adjusted from 0 to 100% to, for example, so that the fluid ejected from at least one of the first and second pumps can be combined in the supply flow path.

[0039] As a result, the ratio of fluid supplied to the actuator from the first and second pumps can be arbitrarily (freely) changed within a range of twice the ejection volume of each pump. Therefore, the flow rate of the fluid supplied to the actuator can be adjusted with high performance.

[0040] (11) Another aspect of the construction machinery of the present invention comprises: a fluid system; and a vehicle body mounted on the fluid system and driven and controlled by the fluid system, the fluid system comprising: a first pump and a second pump; an actuator driven by fluid ejected from the first pump and the second pump to move the vehicle body; and a control valve disposed between the first pump and the second pump and the actuator to adjust the flow rate of the fluid supplied to the actuator or the flow rate of the fluid discharged from the actuator. The control valve comprises: a first inlet throttling valve column having a first inlet throttling flow path communicating with the first pump; a second inlet throttling valve column having a second inlet throttling flow path communicating with the second pump; a supply flow path communicating with the first inlet throttling flow path and the second inlet throttling flow path, and communicating with the supply and discharge ports of the actuator; and an outlet throttling valve column having a flow path communicating with the supply flow path and the supply and discharge ports of the actuator.

[0041] This configuration enables high-precision drive control of construction machinery.

[0042] (12) Another aspect of the actuator drive control method of the present invention includes the following steps: a flow rate adjustment step, in which the combined flow rate of fluids ejected from two pumps respectively connected to each of the inlet throttle valves is adjusted by driving control of the two inlet throttle valves; and a fluid supply step, in which the fluid with the combined flow rate adjusted by the flow rate adjustment step is supplied to the actuator to drive the actuator.

[0043] By employing this control method, the flow rate of the fluid supplied to the actuator can be adjusted with high performance. Therefore, high-precision actuator drive control is possible.

[0044] The effects of the invention

[0045] According to the present invention, the flow rate of the fluid supplied to the actuator can be adjusted with high performance. Attached Figure Description

[0046] Figure 1 This is a schematic diagram of the construction machinery according to the first embodiment of the present invention.

[0047] Figure 2 This is a schematic diagram of the hydraulic system in the first embodiment of the present invention.

[0048] Figure 3 This is an explanatory diagram illustrating an example of the operation of a hydraulic system when the first inlet throttle valve and the second inlet throttle valve are in the first neutral position and the second neutral position, respectively, according to the first embodiment of the present invention.

[0049] Figure 4 This is an explanatory diagram illustrating an example of the action of lifting the boom using a hydraulic system in the first embodiment of the present invention.

[0050] Figure 5 This is an explanatory diagram illustrating an example of the action of lowering the boom using a hydraulic system in the first embodiment of the present invention.

[0051] Figure 6 This is an explanatory diagram illustrating an example of a hydraulic system in the second embodiment of the present invention, in which the boom is held at rest using an independent metering valve.

[0052] Figure 7 This is an explanatory diagram illustrating an example of the action of lifting the boom using a hydraulic system in the second embodiment of the present invention.

[0053] Figure 8 This is an explanatory diagram illustrating an example of the action of lowering the boom using a hydraulic system in the second embodiment of the present invention.

[0054] Figure 9This is an explanatory diagram illustrating an example of a hydraulic system in the third embodiment of the present invention, in which the boom is held at rest using an independent metering valve.

[0055] Figure 10 This is an explanatory diagram illustrating an example of the action of lifting the boom using a hydraulic system in the third embodiment of the present invention.

[0056] Figure 11 This is an explanatory diagram illustrating an example of a hydraulic system in the fourth embodiment of the present invention, in which the boom is held at rest using an independent metering valve.

[0057] Figure 12 This is an explanatory diagram illustrating an example of the action of pressing the boom using a hydraulic system in the fourth embodiment of the present invention.

[0058] Figure 13 This is an explanatory diagram illustrating an example of a hydraulic system in the fifth embodiment of the present invention, in which the boom is held at rest using an independent metering valve.

[0059] Figure 14 This is an explanatory diagram illustrating an example of movement when the boom is pulled by a hydraulic system according to the fifth embodiment of the present invention.

[0060] Figure 15 This is an explanatory diagram illustrating an example of excavation using an independent metering valve to pull the boom in the fifth embodiment of the present invention.

[0061] Figure 16 This is an explanatory diagram illustrating an example of the action of pressing the boom using a hydraulic system in the fifth embodiment of the present invention.

[0062] Explanation of reference numerals in the attached figures

[0063] 2. 151, 171, 181, 191, Independent metering valve (control valve); 3. 173, 183, 193, Valve body (module); 5. 153, 174, 184, 194, First inlet throttle valve stem; 6. 154, 175, 185, 195, Second inlet throttle valve stem; 10. First valve stem orifice (inlet throttle valve stem housing); 11. First inlet throttle flow path; 12. Second inlet throttle flow path; 13. Intermediate section; 15. 186, 196, Outlet throttle valve stem; 21. First notch flow path (flow path); 22. Second notch flow path Path (flow path); 30, Bridging flow path (supply flow path); 100, Construction machinery; 109, 150, 170, 180, 190, Hydraulic system (fluid system); 110A, Pump 1; 110B, Pump 2; 111, Hydraulic actuator (actuator); 113, 116, Hydraulic cylinder (actuator); 120, Tank; 153a, 174a, 184a, First quick recess (recess); 154a, 175a, 185a, Second quick recess (another recess); Hp, Cover port (supply / discharge port); Rp, Rod port (supply / discharge port). Detailed Implementation

[0064] Next, embodiments of the present invention will be described based on the accompanying drawings. In the following embodiments, a hydraulic excavator equipped with a hydraulic system will be used as an example of construction machinery. In the drawings used in the following description, the scale of each component has been appropriately altered to make each component a recognizable size.

[0065] [First Implementation]

[0066] <Construction Machinery>

[0067] Figure 1 This is a schematic diagram of the construction machinery 100 according to the first embodiment.

[0068] like Figure 1 As shown, the construction machinery 100 is, for example, a hydraulic excavator. The construction machinery 100 includes: a slewing body (an example of the body of the claim) 101; a traveling body (an example of the body of the claim) 102; and a hydraulic system 109 mounted on the slewing body 101 and the traveling body 102 for driving control of the slewing body 101 and the traveling body 102.

[0069] The rotating body 101 is mounted on the traveling body 102 in a rotatable manner. The rotating body 101 is equipped with a hydraulic pump 110 and a hydraulic control device 1 for controlling the flow of working oil (an example of the fluid in the claims) injected from the hydraulic pump 110.

[0070] The slewing body 101 includes: a cab 103 for an operator to sit in; a boom 104, one end of which is connected to the slewing body 101 in a swing-free manner; a stick 105, one end of which is connected to the other end (top) of the boom 104 on the opposite side of the slewing body 101 in a swing-free manner; a bucket 106, which is connected to the other end (top) of the stick 105 on the opposite side of the boom 104 in a swing-free manner; and an operating unit 107 disposed in the cab 103.

[0071] The traveling body 102, slewing body 101, boom 104, stick 105, and bucket 106 are driven by various hydraulic actuators 111. The hydraulic actuators 111 are the working parts of the construction machinery 100 driven by working oil supplied from the hydraulic pump 110 via the hydraulic control device 1.

[0072] <Hydraulic System>

[0073] Figure 2 This is a schematic diagram of the hydraulic system 109 according to the first embodiment. Figure 2 This is a schematic diagram of a cross-section including the hydraulic control device 1. Figure 2 In the diagram, it indicates that the first inlet throttle valve 5 and the second inlet throttle valve 6 of the first embodiment are in the first neutral position and the second neutral position, respectively. Additionally, it indicates that the outlet throttle valve 15 of the first embodiment is in the central position.

[0074] like Figure 2 As shown, the hydraulic system (an example of the fluid system of the claim) 109 includes: a hydraulic control device 1; a hydraulic pump 110 that supplies working oil to the hydraulic control device 1; and a hydraulic actuator (an example of the actuator of the claim) 111 that is driven and controlled by the hydraulic control device 1.

[0075] In addition, Figure 2 To simplify the explanation of directions, we will use one side or one end to indicate the right direction in the diagram and the other side or the other end to indicate the left direction. Arrows will be used to represent one side and the other side in each diagram.

[0076] The hydraulic actuator 111 consists of, for example, a hydraulic motor 112 for driving the traveling body 102 or rotating the slewing body 101, and various hydraulic cylinders (an example of the actuator of the claims) 113 for driving the boom 104, stick 105, and bucket 106 (see reference). Figure 1 ).

[0077] The following description uses one hydraulic cylinder 113 from various hydraulic cylinders 113 as a representative example. The hydraulic cylinder 113 of the representative example is a boom drive cylinder for driving the boom 104 selected by the driven boom 104, stick 105, and bucket 106.

[0078] The hydraulic cylinder 113 includes: a cylinder 114; a piston rod 115 disposed within the cylinder 114 in a slidingly movable manner; and a cover port (an example of the supply and discharge port of the claim) Hp and a rod port (an example of the supply and discharge port of the claim) Rp disposed in the cylinder 114.

[0079] The cover port Hp is located at part 114a on the cylinder head side of cylinder 114. The rod port Rp is located at part 114b on the piston rod side of cylinder 114.

[0080] The hydraulic pump 110 is driven by, for example, a prime mover not shown. The hydraulic pump 110 allows for variable injection of hydraulic fluid based on an operation signal from an operating unit 107 located in the operator's cab 103 (see reference). Figure 1 The hydraulic control device 1 is also driven and controlled based on the operation signal of the operation unit 107 (see reference). Figure 1 ).

[0081] There are two hydraulic pumps 110. Hereinafter, one of the two hydraulic pumps 110 will be referred to as "Pump 110A" and the other of the two hydraulic pumps 110 will be referred to as "Pump 110B".

[0082] Pump 110A, for example, is a variable-capacity pump capable of adjusting the amount of working oil injected per revolution within a range of 0 to 100%. Pump 110B, similarly to pump 110A, is also a variable-capacity pump capable of adjusting the amount of working oil injected per revolution within a range of 0 to 100%. Pumps 110A and 110B, for example, have the same pump capacity.

[0083] <Hydraulic Control Device>

[0084] The hydraulic control unit 1 is equipped with various IMVs (Independent Metering Valves) 2 (hereinafter also referred to as "independent metering valves"). The various independent metering valves (an example of the control valves in the claims) 2 control various hydraulic cylinders 113 used to drive the boom 104, stick 105, and bucket 106.

[0085] The following description uses the independent metering valve 2 of the boom 104 as a representative example among various independent metering valves 2. The independent metering valve 2 of the representative example is a valve that controls the hydraulic cylinder 113, which is used to drive the boom 104 selected by the boom 104, stick 105, and bucket 106.

[0086] <Independent Metering Valve (IMV)>

[0087] The independent metering valve 2 has the following main structure: valve body (an example of the module body of the claim) 3; a first inlet throttling valve column 5 in the shape of a round bar, which is housed in the valve body 3; a first inlet throttling solenoid proportional valve 7, which drives and controls the first inlet throttling valve column 5; a second inlet throttling valve column 6 in the shape of a round bar, which is housed in the valve body 3; and a second inlet throttling solenoid proportional valve 8, which drives and controls the second inlet throttling valve column 6.

[0088] That is, the independent metering valve 2 has two independent first inlet throttle valve column 5 and second inlet throttle valve column 6 as inlet throttle valve columns.

[0089] The independent metering valve 2 has the following main components: a cylindrical outlet throttle valve column 15, which is housed in the valve body 3; and a first outlet throttle electromagnetic proportional valve 16 and a second outlet throttle electromagnetic proportional valve 17, which drive and control the outlet throttle valve column 15.

[0090] Furthermore, the independent metering valve 2 is equipped with a control unit 25 that controls the first inlet throttling electromagnetic proportional valve 7, the second inlet throttling electromagnetic proportional valve 8, the first outlet throttling electromagnetic proportional valve 16, and the second outlet throttling electromagnetic proportional valve 17.

[0091] The control unit 25 is implemented by executing a program stored in the program memory using a processor such as a CPU (Central Processing Unit).

[0092] The control unit 25 can be implemented in hardware such as LSI (Large Scale Integration), ASIC (Application Specific Integrated Circuit), or FPGA (Field-Programmable Gate Array), or it can be implemented through software and hardware collaboration.

[0093] The valve body 3 has: a first valve stem hole (an example of the inlet throttle valve stem receiving portion of the claim) 10, which is used to receive the first inlet throttle valve stem 5 and the second inlet throttle valve stem 6; and a first pump port P1, a second pump port P2, a first supply port S1 and a second supply port S2, which are open in the first valve stem hole 10.

[0094] Furthermore, the valve body 3 has: a second valve stem hole 20 for receiving an outlet throttle valve stem 15; and a first tank port T1, a second tank port T2, a first discharge port D1 and a second discharge port D2, which open in the second valve stem hole 20.

[0095] That is, the first inlet throttle valve 5, the second inlet throttle valve 6, and the outlet throttle valve 15 are all located together in one valve body 3.

[0096] The valve body 3 has: a bridging flow path (an example of the supply flow path of the claim) 30, whose cross-section along one direction of the valve body 3 (i.e., the axial direction of the first inlet throttle valve column 5, the second inlet throttle valve column 6, and the outlet throttle valve column 15, hereinafter, there may be cases where this axial direction is simply referred to as the axial direction); a first rod flow path 31, located on one side of the bridging flow path 30; a second rod flow path 32, which communicates with the first rod flow path 31; a first cap flow path 33, located on the other side of the bridging flow path 30; a second cap flow path 34, which communicates with the first cap flow path 33; a first can flow path 35, located on the side of the first rod flow path 31; a second can flow path 36, located on the side of the second cap flow path 34; and a bypass flow path 37, whose cross-section along the axial direction is formed in a U-shape.

[0097] The first valve stem hole 10 and the second valve stem hole 20 are formed along one direction of the valve body 3. The cross-section of the first valve stem hole 10 and the second valve stem hole 20 along the axial direction is circular. The first valve stem hole 10 and the second valve stem hole 20 are formed, for example, in a direction orthogonal to the length direction (i.e., axial direction) of each valve stem hole 10, 20, in a spaced-apart manner.

[0098] The first inlet throttle valve stem 5 and the second inlet throttle valve stem 6 are housed together in one hole of the first valve stem hole 10. The first valve stem hole 10 has a central portion 13 at its axial center. The central portion 13 is a space formed between the first inlet throttle valve stem 5 and the second inlet throttle valve stem 6. The tank 120 communicates with the central portion 13 via the third discharge flow path 137 (see reference). Figure 3 ).

[0099] Pump port P1 is connected to pump 110A via supply path 131. Pump port P2 is connected to pump 110B via supply path 132. Supply port S1 is connected to bridging path 30 via check valve 41. Supply port S2 is connected to bridging path 30 via check valve 42.

[0100] Furthermore, "connection" (or "to connect" as discussed below) refers to the flow of working oil (i.e., fluid). For example, "the first pump port P1 is connected to the first pump 110A via the first supply flow path 131" means that the working oil flows through the connection between the first pump port P1 and the first pump 110A via the first supply flow path 131.

[0101] The first tank port T1 is connected to the tank 120 via the first discharge flow path 135. The second tank port T2 is connected to the tank 120 via the second discharge flow path 136. The first discharge port D1 is connected to the rod port Rp via each rod flow path 31, 32 and the rod-side flow path 133. The second discharge port D2 is connected to the cover port Hp via each cover flow path 33, 34 and the cover-side flow path 134.

[0102] Both ends of the bridging flow path 30 are connected to the first valve column hole 10. The bridging flow path 30 is axially positioned outside the first supply port S1 and the second supply port S2.

[0103] The first rod flow path 31 is axially positioned between one end of the bridging flow path 30 and the first tank flow path 35. The first rod flow path 31 extends in a direction orthogonal to the axial direction. The first rod flow path 31 is connected to the first tank flow path 35 via a first relief valve 45 for releasing excessive high pressure.

[0104] The second rod flow path 32 is disposed between the first valve stem hole 10 and the second valve stem hole 20. The second rod flow path 32 is disposed on the extension line of the first rod flow path 31.

[0105] The first cover flow path 33 is axially positioned between the other end of the bridging flow path 30 and the second tank flow path 36. The first cover flow path 33 extends in a direction intersecting the axial direction. The first cover flow path 33 is connected to the second tank flow path 36 via a second relief valve 46 for releasing excessive high pressure. A locking valve 47 for leakage reduction (a holding valve for preventing the boom 104 from lowering due to inertia) is provided in the first cover flow path 33.

[0106] The second cover flow path 34 is disposed between the first valve stem hole 10 and the second valve stem hole 20. The second cover flow path 34 extends in a direction orthogonal to the axial direction.

[0107] The first can flow path 35 extends outside the first rod flow path 31 in a direction orthogonal to the axial direction. The second can flow path 36 extends outside the first cover flow path 33 in a direction orthogonal to the axial direction. The two ends of the bypass flow path 37 are connected to the second valve stem orifice 20. The bypass flow path 37 is connected to the bypass port G1 via the third check valve 43.

[0108] A first positioning mechanism 50 is provided at one axial end of the valve body 3. The first positioning mechanism 50 includes a first housing 51 that is installed at one axial end of the valve body 3 in such a way as to block one end of the first valve stem hole 10 and the second valve stem hole 20.

[0109] The first housing 51 has: a first receiving chamber 53 connected to one end of the first valve stem hole 10 for receiving the first helical spring 52; and a second receiving chamber 55 connected to one end of the second valve stem hole 20 for receiving the second helical spring 54.

[0110] The first housing 51 has: a first pump flow path 56 extending outside the first receiving chamber 53 and the second receiving chamber 55 in a direction orthogonal to the axial direction; and a first discharge flow path 57 extending outside the first pump flow path 56 in a direction orthogonal to the axial direction.

[0111] A second positioning mechanism 60 is provided at the other end of the valve body 3 in the axial direction. The second positioning mechanism 60 has a second housing 61 installed at the other end of the valve body 3 in such a way as to block the other ends of the first valve stem hole 10 and the second valve stem hole 20.

[0112] The second housing 61 has: a third receiving chamber 63 connected to the other end of the first valve stem bore 10 for receiving the third helical spring 62; and a fourth receiving chamber 65 connected to the other end of the second valve stem bore 20 as a space for guiding working oil.

[0113] The second housing 61 has: a second pump flow path 66 extending outside the third receiving chamber 63 and the fourth receiving chamber 65 in a direction orthogonal to the axial direction; and a second discharge flow path 67 extending outside the second pump flow path 66 in a direction orthogonal to the axial direction.

[0114] A first inlet throttle valve stem 5 is housed on one side of the first valve stem hole 10 of the valve body 3 in a manner that allows it to slide freely in the axial direction. The first inlet throttle valve stem 5 can be positioned in a first neutral position. Figure 2 (as shown in the image) First supply location ( Figure 4 The location shown is used to store the contents of the first neutral location and any supply location between the first supply location and the first supply location.

[0115] The first neutral position is when the intermediate section 13 is at its maximum axial expansion, and the first inlet throttle valve 5 is positioned on one side of the intermediate section 13. The first supply position is when the intermediate section 13 is at its minimum axial narrowing, and the first inlet throttle valve 5 is positioned on one side of the intermediate section 13. The first supply position is the full stroke position of the first inlet throttle valve 5, which connects the first pump 110A to the bridging flow path 30 and supplies the working oil sprayed from the first pump 110A to the bridging flow path 30.

[0116] A second inlet throttle valve stem 6 is housed on the other side of the first valve stem hole 10 of the valve body 3, allowing for free axial sliding movement. The second inlet throttle valve stem 6 can be positioned in a second neutral position. Figure 2 (as shown in the image) 2nd supply location ( Figure 4 The location shown is used to store the contents in any supply location between the second neutral location and the second supply location.

[0117] The second neutral position is when the intermediate section 13 is at its maximum axial expansion, with the second inlet throttle valve 6 positioned on the other side of the intermediate section 13. The second supply position is when the intermediate section 13 is at its minimum axial narrowing, with the second inlet throttle valve 6 positioned on the other side of the intermediate section 13. The second supply position is the full stroke position of the second inlet throttle valve 6, which connects the second pump 110B to the bridging flow path 30 and supplies the working oil sprayed from the second pump 110B to the bridging flow path 30.

[0118] The inlet throttle valve 4 is composed of a first valve stem hole 10, a first inlet throttle valve stem 5, and a second inlet throttle valve stem 6.

[0119] The first inlet throttling valve 5 has a first recess 5a formed, for example, in an annular shape, and a plurality of first shoulders 5b formed on both axial sides (one side and the other side) of the first recess 5a. The first inlet throttling valve 5 can block the flow path or adjust the flow rate by means of the first recess 5a, the first shoulders 5b, etc. The first inlet throttling valve 5 has a first inlet throttling flow path 11 formed, for example, by the first recess 5a, etc.

[0120] The second inlet throttling valve 6 has a second recess 6a formed, for example, in an annular shape, and a plurality of second shoulders 6b formed on both axial sides (one side and the other side) of the second recess 6a. The second inlet throttling valve 6 can block the flow path or adjust the flow rate by means of the second recess 6a, the second shoulders 6b, etc. The second inlet throttling valve 6 has a second inlet throttling flow path 12 formed, for example, by the second recess 6a, etc.

[0121] Figure 3 This is an explanatory diagram illustrating an example of the operation of the hydraulic system 109 when the first inlet throttle valve 5 and the second inlet throttle valve 6 of the first embodiment are in the first neutral position and the second neutral position.

[0122] like Figure 3 As shown, when the first inlet throttle valve column 5 is configured in the first neutral position, it blocks, for example, the first pump port P1 and the first supply port S1 using the first shoulder 5b, etc. When the second inlet throttle valve column 6 is configured in the second neutral position, it blocks, for example, the second pump port P2 and the second supply port S2 using the second shoulder 6b, etc.

[0123] Figure 4 This refers to the method of lifting the boom 104 using a hydraulic system 109 in the first embodiment (see reference). Figure 1 An illustrative diagram illustrating an example of the action during ( ). Figure 4 This diagram illustrates the function of the piston rod 115, which is equivalent to the piston rod 115 that pushes out the hydraulic cylinder 113.

[0124] like Figure 4As shown, when the first inlet throttle valve column 5 is configured to the first supply position, the first pump port P1 is connected to the first supply port S1 via the first inlet throttle flow path 11. When the second inlet throttle valve column 6 is configured to the second supply position, the second pump port P2 is connected to the second supply port S2 via the second inlet throttle flow path 12. As a result, the first pump port P1 and the second pump port P2 are connected to the bridging flow path 30 via the first supply port S1 and the second supply port S2, respectively.

[0125] The bridging flow path 30 is configured to the second discharge position in the outlet throttle valve 15, which will be discussed later. Figure 5 At the position shown, it connects to the rod port Rp via the first gap flow path 21, the second rod flow path 32, and the first rod flow path 31, which will be discussed later.

[0126] like Figure 2 As shown, a first inlet throttling solenoid proportional valve 7 is provided at one axial end of the first inlet throttling valve column 5. A second inlet throttling solenoid proportional valve 8 is provided at the other axial end of the second inlet throttling valve column 6. The first inlet throttling solenoid proportional valve 7 and the second inlet throttling solenoid proportional valve 8 are commonly used valves, and detailed descriptions of their structures are omitted.

[0127] When the first inlet throttling solenoid proportional valve 7 is not energized, the first inlet throttling valve column 5 is positioned in the first neutral position. Figure 2 , Figure 3 (As shown in the image). Because the first inlet throttling solenoid proportional valve 7 is energized, the first inlet throttling valve column 5 is driven based on an electrical signal and positioned in the first supply position (…). Figure 4 , Figure 5 (The location shown).

[0128] The first inlet throttling electromagnetic proportional valve 7 can steplessly control (adjust) the first inlet throttling valve column 5 to any supply position within the range of the first neutral position to the first supply position according to the "current value" of the energized electrical signal (which is proportional to the "current value").

[0129] When the second inlet throttling solenoid proportional valve 8 is not energized, the second inlet throttling valve column 6 is positioned in the second neutral position. Figure 2 , Figure 3 (As shown in the image). Because the second inlet throttling solenoid proportional valve 8 is energized, the second inlet throttling valve column 6 is driven based on an electrical signal and positioned at the second supply position (…). Figure 4 , Figure 5 (The location shown).

[0130] The second inlet throttling electromagnetic proportional valve 8 can steplessly control (adjust) the second inlet throttling valve column 6 to any supply position within the range of the second neutral position to the second supply position, based on the "current value" of the energized electrical signal (which is proportional to the "current value").

[0131] An outlet throttle valve stem 15 is housed in the second valve stem hole 20 of the valve body 3 in a manner that allows for free axial sliding movement. The outlet throttle valve stem 15 is positioned at the axial center of the second valve stem hole 20. Figure 2 , Figure 3 It is stored in three positions: the position shown), the position on one end of the axial direction of the second valve stem hole 20, and the position on the other end of the axial direction of the second valve stem hole 20.

[0132] Hereinafter, the position of one end of the second valve stem hole 20 along its axial direction will be referred to as the first discharge position. Figure 4 The position shown is the position on the other end of the axial direction of the second valve stem hole 20, which is called the second discharge position. Figure 5 (as shown in the image). The outlet throttle valve 14 is composed of the second valve stem hole 20 and the outlet throttle valve stem 15, etc.

[0133] The outlet throttle valve 15 has, for example, a plurality of recesses 15a formed in an annular shape, a plurality of shoulders 15b formed between the recesses 15a, and a plurality of notches 15c formed on the shoulders 15b. The outlet throttle valve 15 can block the flow path or adjust the flow rate by utilizing the recesses 15a, shoulders 15b, and notches 15c.

[0134] The outlet throttle valve 15, for example, has: a first notch flow path (an example of the flow path in the claim) 21 (see reference). Figure 5 ), which is formed by recess 15a, etc.; and second notch flow path (an example of the flow path of the claim) 22 (see Figure 4 It is formed by recesses such as 15a.

[0135] Figure 3 This is an explanatory diagram illustrating an example of the operation of the hydraulic system 109 when the outlet throttle valve 15 of the first embodiment is in the neutral position.

[0136] like Figure 3 As shown, when the outlet throttle valve 15 is positioned in the central position, it uses a shoulder 15b or similar device to block, for example, the first tank port T1, the second tank port T2, the first discharge port D1, and the second discharge port D2. That is, the central position is a neutral position in which the first tank port T1, the second tank port T2, the first discharge port D1, and the second discharge port D2 are blocked using the shoulder 15b or similar device.

[0137] like Figure 4As shown, when the outlet throttle valve 15 is configured to the first discharge position, the first discharge port D1 is connected to the first tank port T1 via the first notch flow path 21. As a result, the rod port Rp is connected to the first tank port T1 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, and the first rod flow path 31.

[0138] When the outlet throttle valve 15 is configured to the first discharge position, the bridging flow path 30 is connected to the second discharge port D2 via the second notch flow path 22. Therefore, the cover port Hp is connected to the bridging flow path 30 via the second notch flow path 22, the second discharge port D2, the second cover flow path 34, and the first cover flow path 33.

[0139] Furthermore, when the outlet throttle valve column 15 is configured to the first discharge position, the second tank port T2 is blocked by the shoulder 15b, etc.

[0140] Figure 5 This refers to the first embodiment where the boom 104 is lowered using a hydraulic system 109 (see reference). Figure 1 An illustrative diagram illustrating an example of the action during ( ). Figure 5 This diagram illustrates the function of the piston rod 115, which is equivalent to pulling the hydraulic cylinder 113 in.

[0141] like Figure 5 As shown, when the outlet throttle valve column 15 is configured to the second discharge position, the second discharge port D2 is connected to the second tank port T2 via the second notch flow path 22.

[0142] As a result, the cap port Hp is connected to the second tank port T2 via the second notch flow path 22, the second discharge port D2, the second cap flow path 34, and the first cap flow path 33.

[0143] When the outlet throttle valve 15 is configured to the second discharge position, the bridging flow path 30 is connected to the first discharge port D1 via the first notch flow path 21. Therefore, the rod port Rp is connected to the bridging flow path 30 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, and the first rod flow path 31.

[0144] Furthermore, when the outlet throttle valve column 15 is configured to the second discharge position, the first tank port T1 is blocked by the shoulder 15b, etc.

[0145] The outlet throttle valve 15 is a valve used to discharge working oil from the cover port Hp, the rod port Rp, and the tank port to the tank 120. The outlet throttle valve 15 controls the amount of working oil discharged from the hydraulic cylinder 113 when discharging working oil to the tank 120.

[0146] For example Figure 2As shown, a first outlet throttling solenoid proportional valve 16 is provided at one end of the outlet throttling valve column 15. A second outlet throttling solenoid proportional valve 17 is provided at the other end of the outlet throttling valve column 15. The first outlet throttling solenoid proportional valve 16 and the second outlet throttling solenoid proportional valve 17 are commonly used valves, just like the first inlet throttling solenoid proportional valve 7 and the second inlet throttling solenoid proportional valve 8; detailed descriptions of their structures are omitted.

[0147] When the first outlet throttling solenoid proportional valve 16 and the second outlet throttling solenoid proportional valve 17 are not energized, the outlet throttling valve column 15 is positioned in the central position.

[0148] The first outlet throttling solenoid proportional valve 16 is energized when the second outlet throttling solenoid proportional valve 17 is de-energized, thereby driving the outlet throttling valve 15 based on the electrical signal and positioning the outlet throttling valve 15 in the second discharge position. Figure 5 (as shown in the image). Among them, the first outlet throttling electromagnetic proportional valve 16 can be steplessly controlled (adjusted) to the second discharge position according to the "current value" (proportional to the "current value") of the energized electrical signal.

[0149] The second outlet throttling solenoid proportional valve 17 is energized when the first outlet throttling solenoid proportional valve 16 is de-energized, thereby driving the outlet throttling valve 15 based on the electrical signal and positioning the outlet throttling valve 15 in the first discharge position. Figure 4 (as shown in the image). Among them, the second outlet throttling electromagnetic proportional valve 17 can be steplessly controlled (adjusted) to the second discharge position according to the "current value" (proportional to the "current value") of the energized electrical signal.

[0150] <Drive control method for hydraulic actuators using independent metering valves and hydraulic systems>

[0151] Next, based on Figures 2-5 This describes the drive control method for the hydraulic actuator 111, which is driven by the independent metering valve 2 and the hydraulic system 109.

[0152] First, based on Figure 2 , Figure 3 This explains how to use independent metering valve 2 to control the boom 104 of construction machinery 100 (refer to...). Figure 1 An example of something remaining stationary.

[0153] like Figure 2 , Figure 3 As shown, the first inlet throttling solenoid proportional valve 7 is set to the unenergized state, and the first inlet throttling valve spool 5 is positioned in the first neutral position. The first pump port P1 and the first supply port S1 are blocked by the first inlet throttling valve spool 5 in the first neutral position.

[0154] The second inlet throttling solenoid proportional valve 8 is further set to an unenergized state, and the second inlet throttling valve column 6 is positioned in the second neutral position. The second pump port P2 and the second supply port S2 are blocked by the second inlet throttling valve column 6 in the second neutral position.

[0155] The first outlet throttling solenoid proportional valve 16 and the second outlet throttling solenoid proportional valve 17 are further set to an unenergized state, and the outlet throttling valve spool 15 is positioned in the central position (i.e., neutral position). The outlet throttling valve spool 15 in the central position is used to block the first tank port T1, the second tank port T2, the first discharge port D1, and the second discharge port D2.

[0156] If pump 110A and pump 110B are driven by a prime mover (not shown), a predetermined flow rate of working oil is sprayed from the discharge ports of each pump 110A, 110B. For example, the sprayed working oil can also return to tank 120 via a return circuit (not shown). In this state, boom 104 (see reference) Figure 1 It is kept at rest.

[0157] Next, based on Figure 2 , Figure 4 This section describes an example of using an independent metering valve 2 to lift the boom 104.

[0158] like Figure 2 , Figure 4 As shown, the first inlet throttle valve 5 is moved in the direction of arrow A1 and positioned in the first supply position. In this case, the first inlet throttle solenoid proportional valve 7 is switched to an energized state, thereby moving the first inlet throttle valve 5 in the direction of the narrowed intermediate portion 13 and positioning it in the first supply position. By positioning the first inlet throttle valve 5 in the first supply position, the first pump port P1 and the first supply port S1 are connected by the first inlet throttle flow path 11.

[0159] The second inlet throttle valve 6 is further moved in the direction of arrow A2 and positioned in the second supply position. In this case, the second inlet throttle solenoid proportional valve 8 is switched to an energized state, thereby moving the second inlet throttle valve 6 in the direction of narrowing the intermediate portion 13 and positioning it in the second supply position. By positioning the second inlet throttle valve 6 in the second supply position, the second pump port P2 and the second supply port S2 are connected by the second inlet throttle flow path 12.

[0160] As a result, the first pump port P1 and the second pump port P2 are connected to the bridging flow path 30 via the first supply port S1 and the second supply port S2, respectively.

[0161] Furthermore, the outlet throttle valve 15 is moved in the direction of arrow A3 and positioned in the first discharge position. In this case, the first outlet throttle solenoid proportional valve 16 is set to an unenergized state, and the second outlet throttle solenoid proportional valve 17 is switched to an energized state, thereby moving the outlet throttle valve 15 in the direction of the first outlet throttle solenoid proportional valve 16 and positioning it in the first discharge position.

[0162] By positioning the outlet throttle valve 15 in the first discharge position, the first discharge port D1 and the first tank port T1 are connected by the first notch flow path 21. As a result, the rod port Rp is connected to the second tank port T1 via the first notch flow path 21, the second discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133.

[0163] Furthermore, by positioning the outlet throttle valve 15 at the first discharge position, the bridging flow path 30 and the second discharge port D2 are connected via the second notch flow path 22. Specifically, the cap port Hp is connected to the bridging flow path 30 via the second notch flow path 22, the second discharge port D2, the second cap flow path 34, the first cap flow path 33, and the cap side flow path 134. In other words, the second notch flow path 22 is connected to the bridging flow path 30, and the second notch flow path 22 is connected to the cap port Hp via the second discharge port D2, etc.

[0164] Furthermore, by positioning the outlet throttle valve 15 at the first discharge position, the shoulder 15b of the outlet throttle valve 15 is used to block the second tank port T2.

[0165] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V1. Additionally, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V2.

[0166] Therefore, the working oil sprayed from the first pump 110A and the working oil sprayed from the second pump 110B merge in the bridging flow path 30.

[0167] The working oil, after merging in the bridging flow path 30, is guided to the second cover flow path 34 via the second notch flow path 22 and the second discharge port D2 as shown by arrow V3. The working oil guided to the second cover flow path 34 flows into the cylinder head side of the cylinder 114 via the first cover flow path 33, the cover side flow path 134, and the cover port Hp as shown by arrow V3.

[0168] On the other hand, the working oil on the rod end side of cylinder 114 is guided to the second rod flow path 32 via rod port Rp, rod side flow path 133, and first rod flow path 31 as shown by arrow V4. The working oil guided to the second rod flow path 32 is discharged (returned to the tank 120) via first discharge port D1, first notch flow path 21, first tank port T1, and first discharge flow path 135 as shown by arrow V4. That is, in the first embodiment, when the boom 104 is raised, the working oil from the first discharge port D1 flows back to the tank 120.

[0169] Therefore, the piston rod 115 of the hydraulic cylinder 113 is pushed out as shown by arrow E1, protruding from the cylinder 114, and the boom 104 (see reference) Figure 1 It was raised.

[0170] Thus, the independent metering valve 2 has two independent inlet throttle valve columns 5 and 6 as inlet throttle valve columns.

[0171] The first inlet throttle valve stem 5 has a first inlet throttle flow path 11 communicating with the first pump 110A. The second inlet throttle valve stem 6 has a second inlet throttle flow path 12 communicating with the second pump 110B. A bridging flow path 30 communicates with the first inlet throttle flow path 11 and the second inlet throttle flow path 12. The bridging flow path 30 is a flow path for supplying working oil injected from at least one of the first pump 110A and the second pump 110B to the cylinder head side or rod end side of the cylinder 114.

[0172] Therefore, the working oil injected from, for example, one first pump 110A can be independently controlled by the first inlet throttle valve 5 and the second inlet throttle valve 6 to guide the working oil injected from, for example, one second pump 110B to the bridging flow path 30. Furthermore, the working oil injected from, for example, two first pumps 110A and second pumps 110B can be independently controlled by the inlet throttle valves 5 and 6 to guide the working oil injected from, for example, two first pumps 110A and second pumps 110B to the bridging flow path 30.

[0173] Among them, the first pump 110A and the second pump 110B have the same pump capacity, and can adjust the spray volume per revolution within the range of 0 to 100%.

[0174] Therefore, according to the independent metering valve 2, the injection volume of each of the first pump 110A and the second pump 110B can be adjusted to twice the injection volume. That is, the proportion of working oil supplied from the first pump 110A and the second pump 110B to the rod end side of the cylinder 114 can be arbitrarily (freely) changed within a range of twice the injection volume of each pump 110A and 110B. As a result, when the boom 104 is raised, the flow rate of working oil flowing into the rod end side of the cylinder 114 can be adjusted with high performance.

[0175] Next, based on Figure 2 , Figure 5 This illustrates an example of lowering the boom 104 using an independent metering valve 2.

[0176] like Figure 2 , Figure 5 As shown, similar to the case of lifting boom 104, the first inlet throttle valve 5 and the second inlet throttle valve 6 are held in the first supply position and the second supply position, respectively. In this state, the outlet throttle valve 15 is moved in the direction of arrow A4 to be positioned in the second discharge position. In this case, by setting the second outlet throttle solenoid proportional valve 17 to the de-energized state and switching the first outlet throttle solenoid proportional valve 16 to the energized state, the outlet throttle valve 15 is moved in the direction towards the second outlet throttle solenoid proportional valve 17 to be positioned in the second discharge position.

[0177] By positioning the outlet throttle valve 15 at the second discharge position, the second discharge port D2 is connected to the second tank port T2 via the second notch flow path 22. As a result, the cap port Hp is connected to the second tank port T2 via the second notch flow path 22, the second discharge port D2, the second cap flow path 34, the first cap flow path 33, and the cap side flow path 134.

[0178] Furthermore, by positioning the outlet throttle valve 15 at the second discharge position, the bridging flow path 30 is connected to the first discharge port D1 via the first notch flow path 21. Specifically, the rod port Rp is connected to the bridging flow path 30 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133. In other words, the first notch flow path 21 is connected to the bridging flow path 30, and the first notch flow path 21 is connected to the rod port Rp via the first discharge port D1, etc.

[0179] Furthermore, by positioning the outlet throttle valve 15 at the second discharge position, the first tank port T1 is blocked by the shoulder 15b of the outlet throttle valve 15.

[0180] In this state, similar to the case of raising the boom 104, the working oil injected from the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V1. Additionally, the working oil injected from the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V2.

[0181] Therefore, the working oil sprayed from the first pump 110A and the working oil sprayed from the second pump 110B merge in the bridging flow path 30.

[0182] The working oil, after merging in the bridging flow path 30, is guided to the second rod flow path 32 via the first notch flow path 21 and the first discharge port D1 as shown by arrow V5. The working oil guided to the second rod flow path 32 flows into the rod end side of the cylinder 114 via the first rod flow path 31, the rod side flow path 133, and the rod port Rp as shown by arrow V5.

[0183] On the other hand, the working oil on the cylinder head side of cylinder 114 is guided to the second cylinder head flow path 34 via the cylinder head port Hp, the cylinder head flow path 134, and the first cylinder head flow path 33 as shown by arrow V6. The working oil guided to the second cylinder head flow path 34 is discharged to the tank 120 (returning to the tank 120) via the second discharge port D2, the second notch flow path 22, the second tank port T2, and the second discharge flow path 136 as shown by arrow V6. That is, in the first embodiment, when lowering the boom 104 (see...) Figure 1 In the case of ), the working oil from the second discharge port D2 is returned to the tank 120.

[0184] Thus, the piston rod 115 of the hydraulic cylinder 113 is pulled in as shown by arrow E2, in a manner that pushes it into the cylinder 114, and the boom 104 (see reference) Figure 1 () was reduced.

[0185] Similar to the case of lifting boom 104, the independent metering valve 2 can independently control the first inlet throttle valve 5 and the second inlet throttle valve 6. By independently controlling each inlet throttle valve 5, 6, working oil injected from at least one of, for example, the first pump 110A and the second pump 110B can be directed to the bridging flow path 30.

[0186] Therefore, the injection volume of each of the first pump 110A and the second pump 110B can be adjusted to twice the injection volume. That is, the proportion of working oil supplied from the first pump 110A and the second pump 110B to the cylinder head side of the cylinder 114 can be arbitrarily (freely) changed within a range of twice the injection volume of each pump 110A and 110B. As a result, when lowering the boom 104, the flow rate of working oil flowing into the cylinder head side of the cylinder 114 can be adjusted with high performance.

[0187] Thus, the drive control method for the hydraulic actuator 111 includes the following steps: a flow adjustment step, in which the combined flow rate of the working oil injected from the two pumps 110A and 110B is adjusted by driving control of the two inlet throttle valve columns 5 and 6; and a fluid supply step, in which the working oil whose combined flow rate has been adjusted by the flow adjustment step is supplied to the hydraulic actuator 111 to drive the hydraulic actuator 111.

[0188] The following embodiments also have the same procedures, therefore, the statements about the flow adjustment procedure and the fluid supply procedure are omitted in the following embodiments.

[0189] As explained above, the independent metering valve 2 of the hydraulic system 109 in the first embodiment has two independent first inlet throttle valve columns 5 and second inlet throttle valve columns 6 as inlet throttle valve columns.

[0190] The first inlet throttle valve stem 5 has a first inlet throttle flow path 11 communicating with the first pump 110A. The second inlet throttle valve stem 6 has a second inlet throttle flow path 12 communicating with the second pump 110B. A bridging flow path 30 communicates with the first inlet throttle flow path 11 and the second inlet throttle flow path 12. The bridging flow path 30 is a flow path for supplying working oil injected from at least one of the first pump 110A and the second pump 110B to the rod end side or cylinder head side of the cylinder 114.

[0191] Therefore, based on the drive control method of the independent metering valve 2, the hydraulic system 109, and the hydraulic actuator 111, the injection volume of each of the first pump 110A and the second pump 110B can be adjusted to twice the injection volume. That is, the proportion of working oil supplied from the first pump 110A and the second pump 110B to the rod end side of the cylinder 114 can be arbitrarily (freely) changed within a range of twice the injection volume of each pump 110A and 110B. As a result, when raising or lowering the boom 104, the flow rate of working oil flowing into the rod end side or cylinder head side of the cylinder 114 can be adjusted with high performance.

[0192] Furthermore, the first inlet throttle valve stem 5 and the second inlet throttle valve stem 6 are housed together in one hole of the first valve stem hole 10. As a result, the number of first valve stem holes 10 can be reduced, and the structure of the hydraulic system 109 and the independent metering valve 2 can be simplified.

[0193] Furthermore, the first valve stem orifice 10 has a central portion 13 at its axial center. That is, the central portion 13 is formed in the middle between the first inlet throttle valve stem 5 and the second inlet throttle valve stem 6. The tank 120 is connected to the central portion 13 via the third discharge flow path 137. Therefore, corresponding to the volume change of the central portion 13 caused by the movement of the first inlet throttle valve stem 5 and the second inlet throttle valve stem 6, the working oil can move between the central portion 13 and the tank 120.

[0194] Specifically, when the first inlet throttle valve column 5 and the second inlet throttle valve column 6 move in a manner that reduces the volume of the intermediate section 13, the working oil in the intermediate section 13 can be discharged into the tank 120. As a result, it is possible to prevent the pressure of the working oil in the intermediate section 13 from increasing and making it difficult for each inlet throttle valve column 5 and 6 to move. Thus, the first inlet throttle valve column 5 and the second inlet throttle valve column 6 can move smoothly inside the first valve column orifice 10.

[0195] Furthermore, by configuring the outlet throttle valve 15 in the first discharge position ( Figure 4(as shown in the figure) enables the second gap flow path 22 to be connected to the bridging flow path 30, and enables the second discharge port D2 to be connected to the cover port Hp.

[0196] Furthermore, by configuring the outlet throttle valve 15 in the second discharge position ( Figure 5 (as shown in the figure) enables the first gap flow path 21 to be connected to the bridging flow path 30, and enables the first gap flow path 21 to be connected to the rod port Rp via the first discharge port D1, etc.

[0197] The first inlet throttling flow path 11 of the first inlet throttling valve column 5 and the second inlet throttling flow path 12 of the second inlet throttling valve column 6 are connected to the bridging flow path 30. Therefore, the outlet throttling valve column 15 can universally accommodate both the first inlet throttling valve column 5 and the second inlet throttling valve column 6. This reduces the number of outlet throttling valve columns 15 to one, simplifying the structure of the hydraulic system 109 and the independent metering valve 2.

[0198] Furthermore, the first inlet throttle valve 5, the second inlet throttle valve 6, and the outlet throttle valve 15 are all housed in a single valve body 3. This reduces the number of valve bodies 3 and simplifies the hydraulic system 109 and the independent metering valve 2, resulting in a more compact design.

[0199] The following is based on Figures 6 to 16 The independent metering valve, hydraulic system, and drive control method of hydraulic actuator in embodiments 2 to 4 are described. Furthermore, in embodiments 2 to 4, structures identical or similar to those in embodiment 1 are labeled with the same reference numerals, and detailed descriptions are omitted.

[0200] [Second Implementation]

[0201] <Independent Metering Valve>

[0202] Figure 6 This is an explanatory diagram illustrating an example of a hydraulic system (an example of a fluid system according to the claim) 150 when the boom 104 is held to a stationary state using an independent metering valve (an example of the control valve in the claim) 151 according to the second embodiment. Figure 6 This is an explanatory diagram that is equivalent to keeping the piston rod 115 of the hydraulic cylinder 113 stationary.

[0203] like Figure 6 As shown, the independent metering valve 151 of the second embodiment includes a first inlet throttle valve column 153 and a second inlet throttle valve column 154. The other structures of the independent metering valve 151 of the second embodiment are the same as those of the independent metering valve 2 of the first embodiment described above.

[0204] The first inlet throttle valve stem 153 has a first quick recess (an example of the recess in the claim) 153a, and the other structures are the same as those of the first inlet throttle valve stem 5 in the first embodiment. The first quick recess 153a is formed, for example, by utilizing a stepped portion that is recessed relative to the first shoulder 153b over the entire circumference. Alternatively, the first quick recess 153a may also be formed using a stepped portion and a notch, for example.

[0205] The first quick recess 153a is formed at a position closer to one side than one end of the bridging flow path 30. The first quick recess 153a is positioned at the first neutral position of the first inlet throttling valve column 153. Figure 6 When positioned as shown, the entire assembly is located between the first link flow path 31 and the second link flow path 32.

[0206] Figure 7 This refers to the second embodiment where the boom 104 is raised using a hydraulic system 150 (see reference). Figure 1 An illustrative diagram illustrating an example of the action during ( ). Figure 7 This diagram illustrates the function of the piston rod 115, which is equivalent to the piston rod 115 that pushes out the hydraulic cylinder 113.

[0207] Figure 8 This refers to the second embodiment where the boom 104 is lowered using a hydraulic system 150 (see reference). Figure 1 An illustrative diagram illustrating an example of the action during ( ). Figure 8 This diagram illustrates the function of the piston rod 115, which is equivalent to pulling the hydraulic cylinder 113 in.

[0208] For example Figure 7 , Figure 8 As shown, the first inlet throttle valve column 153 is configured at the first supply position ( Figure 7 , Figure 8 When the position shown is such that the first quick recess 153a is partially disposed between the first rod flow path 31 and the second rod flow path 32, the first quick recess 153a can be used to ensure a large cross-sectional area of ​​the flow path between the first rod flow path 31 and the second rod flow path 32.

[0209] The first quick recess 153a is positioned at the second discharge position on the outlet throttle valve 15. Figure 8 In the state shown, the first quick recess 153a is connected to the bridging flow path 30 via the second rod flow path 32, the first discharge port D1, and the first notch flow path 21. Moreover, when the outlet throttle valve column 15 is configured to the second discharge position, the first quick recess 153a is connected to the rod port Rp via the first rod flow path 31 and the rod side flow path 133.

[0210] That is, the first quick recess 153a connects the bridging flow path 30 with the rod port Rp (specifically, the rod end side of the cylinder 114) when the outlet throttle valve column 15 is configured to the second discharge position.

[0211] On the other hand, the first quick recess 153a is positioned at the first discharge position on the outlet throttle valve column 15. Figure 7 In the position shown, the first quick recess 153a is connected to the tank 120 via the second rod flow path 32, the first discharge port D1, the first notch flow path 21, the first tank port T1, and the first discharge flow path 135. Furthermore, when the outlet throttle valve column 15 is positioned at the first discharge position, the first quick recess 153a is connected to the rod port Rp via the first rod flow path 31 and the rod-side flow path 133.

[0212] That is, the first quick recess 153a connects the rod port Rp (specifically, the rod end side of the cylinder 114) to the tank 120 when the outlet throttle valve column 15 is configured to the first discharge position.

[0213] like Figure 6 As shown, the second inlet throttle valve stem 154 has a second quick recess (an example of another recess in the claim) 154a, and the other structures are the same as those of the second inlet throttle valve stem 6 in the first embodiment. The second quick recess 154a is formed, for example, using a stepped portion that is recessed relative to the second shoulder 154b over the entire circumference. Alternatively, the second quick recess 154a can also be formed using a stepped portion and a notch.

[0214] The second quick recess 154a is formed at a position on the opposite side of the other end of the bridging flow path 30. The second quick recess 154a is positioned at the second neutral position of the second inlet throttle valve column 154. Figure 6 When positioned as shown, the entire structure is positioned between the first cover flow path 33 and the second cover flow path 34.

[0215] like Figure 7 , Figure 8 As shown, the second inlet throttle valve column 154 is configured at the second supply position. Figure 7 , Figure 8 When the position shown is such that the second quick recess 154a is partially disposed between the first cover flow path 33 and the second cover flow path 34, the cross-sectional area of ​​the flow path between the first cover flow path 33 and the second cover flow path 34 can be ensured to be large by utilizing the second quick recess 154a.

[0216] The second quick recess 154a is configured at the second discharge position on the outlet throttle valve 15. Figure 8 In the state shown, the second quick recess 154a is connected to the tank 120 via the second cover flow path 34, the second discharge port D2, the second notch flow path 22, the second tank port T2, and the second discharge flow path 136. Moreover, the second quick recess 154a is connected to the cover port Hp via the first cover flow path 33 and the cover side flow path 134 when the outlet throttle valve column 15 is configured to the second discharge position.

[0217] That is, the second quick recess 154a connects the cover port Hp (specifically, the cylinder cover side of cylinder 114) to the tank 120 when the outlet throttle valve column 15 is configured to the second discharge position.

[0218] Furthermore, the second quick recess 154a is positioned at the first discharge position on the outlet throttle valve column 15. Figure 7 In the state shown, the second quick recess 154a is connected to the bridging flow path 30 via the second cover flow path 34, the second discharge port D2, and the second notch flow path 22. Moreover, when the outlet throttle valve column 15 is configured to the first discharge position, the second quick recess 154a is connected to the cover port Hp via the first cover flow path 33 and the cover side flow path 134.

[0219] That is, the second quick recess 154a connects the bridging flow path 30 to the cover port Hp (specifically, the cylinder head side of cylinder 114) when the outlet throttle valve column 15 is configured to the first discharge position.

[0220] <Drive control method for hydraulic actuators using independent metering valves and hydraulic systems>

[0221] Next, based on Figures 6-8 This describes a method for driving and controlling a hydraulic actuator 111 (hydraulic cylinder 113) via an independent metering valve 151 and a hydraulic system 150.

[0222] First, based on Figure 6 This explains how the independent metering valve 151 is used to control the boom 104 of the construction machinery 100 (refer to...). Figure 1 An example of something remaining stationary.

[0223] For example Figure 6 As shown, the first inlet throttle valve 153 is positioned in the first neutral position, thereby blocking the first pump port P1 and the first supply port S1. Furthermore, the second inlet throttle valve 154 is positioned in the second neutral position, thereby blocking the second pump port P2 and the second supply port S2.

[0224] Furthermore, the outlet throttle valve 15 is positioned in the center to block the first tank port T1, the second tank port T2, the first discharge port D1, and the second discharge port D2.

[0225] In this state, the working oil sprayed from the respective spray ports of the first pump 110A and the second pump 110B returns to the tank 120 via a return loop (not shown), for example, the boom 104 (see reference). Figure 1 It is kept at rest.

[0226] Next, based on Figure 7This section describes an example of using an independent metering valve 151 to lift the boom 104.

[0227] like Figure 7 As shown, by moving the first inlet throttle valve 153 in the direction of arrow A5 to the first supply position, the first pump port P1 is connected to the first supply port S1 via the first inlet throttle flow path 11. Furthermore, by moving the second inlet throttle valve 6 in the direction of arrow A6 to the second supply position, the second pump port P2 is connected to the second supply port S2 via the second inlet throttle flow path 12.

[0228] As a result, the first pump port P1 and the second pump port P2 are connected to the bridging flow path 30 via the first supply port S1 and the second supply port S2, respectively.

[0229] Furthermore, the outlet throttle valve 15 is positioned in the first discharge position by moving it in the direction of arrow A7. With the outlet throttle valve 15 positioned in the first discharge position, the first discharge port D1 and the first tank port T1 are connected by the first notch flow path 21. As a result, the rod port Rp is connected to the first tank port T1 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133.

[0230] Furthermore, by positioning the outlet throttle valve 15 at the first discharge position, the second notch flow path 22 is connected to the bridging flow path 30, and the second notch flow path 22 is connected to the cover port Hp via the second discharge port D2, etc. Specifically, the cover port Hp is connected to the bridging flow path 30 via the second notch flow path 22, the second discharge port D2, the second cover flow path 34, the first cover flow path 33, and the cover side flow path 134, etc.

[0231] Furthermore, the outlet throttle valve 15 configured at the second discharge position is used to block the second tank port T2.

[0232] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V7. Furthermore, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V8. Therefore, the working oils ejected from the first pump 110A and the second pump 110B merge in the bridging flow path 30.

[0233] The working oil after merging is guided to the second cover flow path 34 via the second notch flow path 22 and the second discharge port D2 as shown by arrow V9. The working oil guided to the second cover flow path 34 flows into the cylinder head side of the cylinder 114 via the first cover flow path 33, the cover side flow path 134, and the cover port Hp as shown by arrow V9.

[0234] The second quick recess 154a is located between the first cover flow path 33 and the second cover flow path 34. Therefore, the cross-sectional area of ​​the flow path between the first cover flow path 33 and the second cover flow path 34 can be ensured to be large. This reduces the pressure loss of the working oil supplied from the bridging flow path 30 to the cylinder head side of the cylinder 114. In other words, working oil can be supplied to the cylinder head side of the cylinder 114 efficiently.

[0235] On the other hand, the working oil on the rod end side of cylinder 114 is guided to the second rod flow path 32 via rod port Rp, rod side flow path 133, and first rod flow path 31 as shown by arrow V10. The working oil guided to the second rod flow path 32 is discharged to tank 120 (returning to tank 120) via first discharge port D1, first notch flow path 21, first tank port T1, and first discharge flow path 135 as shown by arrow V10.

[0236] The first quick recess 153a is located between the first rod flow path 31 and the second rod flow path 32. Therefore, the cross-sectional area of ​​the flow path between the first rod flow path 31 and the second rod flow path 32 can be ensured to be large. As a result, the flow rate of the working oil returning from the rod end side of the cylinder 114 to the tank 120 can be increased, and the working oil can be returned to the tank 120 from the rod end side efficiently.

[0237] By supplying working oil to the cylinder head side of cylinder 114, the working oil returns to the reservoir 120 from the rod end side, and the piston rod 115 is pushed out of cylinder 114 as shown by arrow E3, and the boom 104 (see reference) Figure 1 It was raised.

[0238] Next, based on Figure 8 This illustrates an example of lowering the boom 104 using an independent metering valve 151.

[0239] like Figure 8 As shown, similar to the case of lifting boom 104, the first inlet throttle valve 153 and the second inlet throttle valve 154 are held in the first supply position and the second supply position, respectively. In this state, the outlet throttle valve 15 is moved in the direction of arrow A8 to the second discharge position, and the second discharge port D2 is connected to the second tank port T2 by the second notch flow path 22. As a result, the cap port Hp is connected to the second tank port T2 via the second notch flow path 22, the second discharge port D2, the second cap flow path 34, the first cap flow path 33, and the cap side flow path 134.

[0240] Furthermore, by positioning the outlet throttle valve 15 at the second discharge position, the first notch flow path 21 is connected to the bridging flow path 30, and the first notch flow path 21 is connected to the rod port Rp via the first discharge port D1, etc. Specifically, the rod port Rp is connected to the bridging flow path 30 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133, etc.

[0241] Furthermore, the outlet throttle valve 15 configured at the second discharge position is used to block the first tank port T1.

[0242] In this state, similar to the case of lifting boom 104, the working oil sprayed from pump 110A and pump 110B merges in bridging flow path 30. The merged working oil is guided to second rod flow path 32 via first notch flow path 21 and first discharge port D1 as shown by arrow V11. The working oil guided to second rod flow path 32 flows into the rod end side of cylinder 114 via first rod flow path 31, rod side flow path 133, and rod port Rp as shown by arrow V11.

[0243] The first quick recess 153a is located between the first rod flow path 31 and the second rod flow path 32. Therefore, the cross-sectional area of ​​the flow path between the first rod flow path 31 and the second rod flow path 32 can be ensured to be large. This reduces the pressure loss of the working oil supplied from the bridging flow path 30 to the rod end side of the cylinder 114. In other words, working oil can be supplied to the rod end side of the cylinder 114 efficiently.

[0244] On the other hand, the working oil on the cylinder head side of cylinder 114 is guided to the second cylinder head flow path 34 via the cylinder head port Hp, the cylinder head flow path 134, and the first cylinder head flow path 33 as shown by arrow V12. The working oil guided to the second cylinder head flow path 34 is discharged to the tank 120 (returning to the tank 120) via the second discharge port D2, the second notch flow path 22, the second tank port T2, and the second discharge flow path 136 as shown by arrow V12.

[0245] The second quick recess 154a is located between the first cover flow path 33 and the second cover flow path 34. Therefore, the cross-sectional area of ​​the flow path between the first cover flow path 33 and the second cover flow path 34 can be ensured to be large. As a result, the flow rate of working oil returning from the cylinder head side of the cylinder 114 to the tank 120 can be increased, and the working oil can be returned to the tank 120 from the cylinder head side efficiently.

[0246] Thus, by supplying working oil to the rod end side of cylinder 114, the working oil returns from the cylinder head side to the reservoir 120, and piston rod 115 is pulled into cylinder 114 as shown by arrow E4, and boom 104 (see reference) Figure 1 () was reduced.

[0247] As explained above, the independent metering valve 151 of the hydraulic system 150 in the second embodiment is similar to that in the first embodiment, having two independent first inlet throttle valve columns 153 and second inlet throttle valve columns 154 as inlet throttle valve columns.

[0248] Therefore, based on the drive control method of the independent metering valve 151, the hydraulic system 150 and the hydraulic actuator 111 (hydraulic cylinder 113), when raising or lowering the boom 104, the flow rate of the working oil flowing into the rod end side or cylinder head side of the cylinder 114 can be adjusted with high performance, similar to the first embodiment.

[0249] Furthermore, the drive control method of the independent metering valve 151, hydraulic system 150, and hydraulic actuator 111 (hydraulic cylinder 113) in the second embodiment achieves the same effect as in the first embodiment.

[0250] Furthermore, the independent metering valve 151 of the hydraulic system 150 in the second embodiment has a first quick recess 153a in the first inlet throttle valve column 153 and a second quick recess 154a in the second inlet throttle valve column 154.

[0251] Therefore, according to the drive control method of the independent metering valve 151, the hydraulic system 150 and the hydraulic actuator 111 (hydraulic cylinder 113), as described above, the pressure loss of the working oil flowing into the hydraulic cylinder 113 can be reduced and the flow rate of the working oil discharged from the hydraulic cylinder 113 can be increased.

[0252] [Third Implementation]

[0253] <Independent Metering Valve>

[0254] Figure 9 This is an explanatory diagram illustrating an example of a hydraulic system (an example of a fluid system according to the claim) 170 in the third embodiment, which uses an independent metering valve (an example of the control valve in the claim) 171 to hold the boom 104 to a stationary state. Figure 9 This is an explanatory diagram that is equivalent to keeping the piston rod 115 of the hydraulic cylinder 113 stationary.

[0255] like Figure 9 As shown, the independent metering valve 171 of the third embodiment includes a valve body (an example of the module body of the claim) 173, a first inlet throttle valve column 174, and a second inlet throttle valve column 175. The other structures of the independent metering valve 171 of the third embodiment are the same as those of the independent metering valve 2 of the first embodiment.

[0256] Valve body 173 has a third can port T3 and a fourth can port T4, and its other structure is the same as that of valve body 3 in the first embodiment. The third can port T3 is located on one side of the second rod flow path 32, in the first valve stem hole 10 (refer to...). Figure 2 The third tank port T3 is connected to the tank 120 via the fourth discharge flow path 177. The fourth tank port T4 is located on the other side of the second cover flow path 34 and opens at the first valve pillar hole 10. The fourth tank port T4 is connected to the tank 120 via the fifth discharge flow path 178.

[0257] The first inlet throttle valve stem 174 has a first quick recess (an example of the recess of the claim) 174a, and the other structures are the same as those of the first inlet throttle valve stem 5 of the first embodiment. The first quick recess 174a is formed, for example, by utilizing a stepped portion that is recessed relative to the first shoulder 174b over the entire circumference. In addition, the first quick recess 174a may also be formed, for example, by utilizing a stepped portion and a notch.

[0258] The first quick-access recess 174a is formed at a position closer to one side than one end of the bridging flow path 30. The first quick-access recess 174a is positioned at the first neutral position of the first inlet throttling valve column 174. Figure 9 When it reaches the position shown, it is connected to the third tank port T3.

[0259] Figure 10 This refers to the third embodiment where the boom 104 is raised using a hydraulic system 170 (see reference). Figure 1 An illustrative diagram illustrating an example of the action during ( ). Figure 10 This diagram illustrates the function of the piston rod 115, which is equivalent to the piston rod 115 that pushes out the hydraulic cylinder 113.

[0260] like Figure 10 As shown, the first inlet throttle valve column 174 is configured to the first supply position ( Figure 10 When the position shown is such that the other side of the first quick recess 174a is partially positioned between the first rod flow path 31 and the second rod flow path 32, a portion of one side of the first quick recess 174a is connected to the third can port T3.

[0261] Therefore, the first quick recess 174a connects the first rod flow path 31 with the third can port T3. Thus, the rod port Rp (specifically, the rod end side of cylinder 114) is connected to can 120 via the rod side flow path 133, the first rod flow path 31, the first quick recess 174a, the third can port T3, and the fourth discharge flow path 177.

[0262] Furthermore, the outlet throttle valve 15 is configured to the first discharge position ( Figure 10In the position shown, the rod end Rp is connected to the second rod flow path 32 via the rod-side flow path 133 and the first rod flow path 31. Furthermore, the second rod flow path 32 is connected to the tank 120 via the first discharge port D1, the first notch flow path 21, the first tank port T1, and the first discharge flow path 135. That is, the rod end Rp (specifically, the rod end side of the cylinder 114) is connected to the tank 120 via the first notch flow path 21 of the outlet throttle valve 15 when the outlet throttle valve 15 is positioned at the first discharge position.

[0263] The second inlet throttle valve stem 175 has a second quick recess (an example of another recess in the claim) 175a. The other structures of the second inlet throttle valve stem 175 are the same as those of the second inlet throttle valve stem 6 in the first embodiment. The second quick recess 175a is formed, for example, using a stepped portion that is recessed relative to the second shoulder 175b over the entire circumference. Furthermore, the second quick recess 175a may also be formed, for example, using a stepped portion and a notch.

[0264] The second quick recess 175a is formed at a position on the opposite side of the other end of the bridging flow path 30. The second quick recess 175a is positioned at the second neutral position of the second inlet throttle valve column 175. Figure 9 When positioned as shown, it is configured between the first cover flow path 33 and the second cover flow path 34.

[0265] like Figure 10 As shown, the second inlet throttle valve column 175 is configured at the second supply position ( Figure 10 When the position shown is reached, a portion of one side of the second quick recess 175a is connected to the bridging flow path 30. At this time, a portion of the other side of the first quick recess 174a is connected to the first cover flow path 33. Therefore, the second quick recess 175a connects the bridging flow path 30 and the first cover flow path 33. Thus, the bridging flow path 30 is connected to the cover port Hp (specifically, the cylinder head side of the cylinder 114) via the second quick recess 175a, the first cover flow path 33, and the cover-side flow path 134.

[0266] Furthermore, the outlet throttle valve 15 is configured to the first discharge position ( Figure 10 In the state shown (position), the bridging flow path 30 is connected to the second cover flow path 34 via the second notch flow path 22 and the second discharge port D2. The second cover flow path 34 is connected to the cover port Hp via the first cover flow path 33 and the cover side flow path 134. That is, when the outlet throttle valve column 15 is configured to the first discharge position, the bridging flow path 30 is connected to the cover port Hp (specifically, the cylinder head side of cylinder 114) via the second notch flow path 22.

[0267] <Drive control method for hydraulic actuators using independent metering valves and hydraulic systems>

[0268] Next, based on Figure 9 , Figure 10 This describes a method for driving and controlling a hydraulic actuator 111 (hydraulic cylinder 113) via an independent metering valve 171 and a hydraulic system 170.

[0269] First, based on Figure 9 This explains how the independent metering valve 171 is used to control the boom 104 of the construction machinery 100 (refer to...). Figure 1 An example of something remaining stationary.

[0270] like Figure 9 As shown, the first inlet throttle valve 174 is positioned in the first neutral position, thereby blocking the first pump port P1 and the first supply port S1. Additionally, the second inlet throttle valve 175 is positioned in the second neutral position, thereby blocking the second pump port P2 and the second supply port S2.

[0271] Furthermore, the outlet throttle valve 15 is positioned in the center ( Figure 9 (as shown in the figure) and use the outlet throttle valve column 15 to block the first tank port T1, the second tank port T2, the first discharge port D1, and the second discharge port D2.

[0272] In this state, the working oil sprayed from the respective spray ports of the first pump 110A and the second pump 110B returns to the tank 120 via a return loop (not shown), for example, the boom 104 (see reference). Figure 1 It is kept at rest.

[0273] Next, based on Figure 10 This section describes an example of using an independent metering valve 171 to lift the boom 104.

[0274] For example Figure 10 As shown, by moving the first inlet throttle valve column 174 in the direction of arrow A9 to the first supply position, the first pump port P1 is connected to the first supply port S1 by using the first inlet throttle flow path 11.

[0275] Furthermore, by positioning the first inlet throttle valve column 174 in the first supply position, the first rod flow path 31 and the third tank port T3 are connected via the first quick recess 174a.

[0276] As a result, the rod port Rp is connected to the third can port T3 via the first quick recess 174a, the first rod flow path 31, and the rod side flow path 133.

[0277] Furthermore, by moving the second inlet throttle valve 175 in the direction of arrow A10 to the second supply position, the second pump port P2 is connected to the second supply port S2 via the second inlet throttle flow path 12. As a result, the first pump port P1 and the second pump port P2 are connected to the bridging flow path 30 via the first supply port S1 and the second supply port S2, respectively.

[0278] Furthermore, by positioning the second inlet throttle valve column 6 at the second supply position, the bridging flow path 30 is connected to the first cover flow path 33 via the second quick recess 175a.

[0279] As a result, the cap port Hp is connected to the bridging flow path 30 via the second quick recess 175a, the first cap flow path 33, and the cap side flow path 134.

[0280] Additionally, the outlet throttle valve 15 is positioned in the first discharge position by moving it in the direction of arrow A11. With the outlet throttle valve 15 positioned in the first discharge position, the first discharge port D1 and the first tank port T1 are connected by the first notch flow path 21.

[0281] As a result, the rod port Rp is connected to the first tank port T1 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod side flow path 133.

[0282] Furthermore, by positioning the outlet throttle valve 15 at the first discharge position, the second notch flow path 22 is connected to the bridging flow path 30, and the second notch flow path 22 is connected to the cover port Hp via the second discharge port D2, etc. Specifically, the cover port Hp is connected to the bridging flow path 30 via the second notch flow path 22, the second discharge port D2, the second cover flow path 34, the first cover flow path 33, and the cover side flow path 134, etc.

[0283] In addition, the outlet throttle valve 15 configured to the first discharge position is used to block the second tank port T2.

[0284] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V13. Furthermore, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V14. Therefore, the working oils ejected from the first pump 110A and the second pump 110B merge in the bridging flow path 30.

[0285] A portion of the merged working oil is guided to the first cover flow path 33 via the second quick recess 175a as shown by arrow V15. Furthermore, the remaining portion of the merged working oil is guided to the first cover flow path 33 via the second notch flow path 22, the second discharge port D2, and the second cover flow path 34 as shown by arrow V16. Hereinafter, the portion of the merged working oil will be referred to as "first working oil," and the remaining portion will be referred to as "second working oil."

[0286] The first working oil and the second working oil, which are guided to the first cover flow path 33, flow into the cylinder head side of the cylinder 114 via the cover side flow path 134 and the cover port Hp as shown by arrow V17.

[0287] In this way, the first working oil in the working oil after merging in the bridging flow path 30 is guided to the first cover flow path 33 via the second quick recess 175a instead of passing through the second notch flow path 22 of the outlet throttle valve column 15. This reduces the pressure loss of the working oil supplied from the bridging flow path 30 to the cylinder head side of the cylinder 114. That is, working oil can be supplied to the cylinder head side of the cylinder 114 efficiently.

[0288] On the other hand, the working oil on the rod end side in cylinder 114 is guided to the first rod flow path 31 via the rod port Rp and the rod side flow path 133 as shown by arrow V18. A portion of the working oil guided to the first rod flow path 31 is discharged (returned) to the tank 120 via the first quick recess 174a and the fourth discharge flow path 177 as shown by arrow V19.

[0289] Furthermore, the remaining portion of the working oil guided to the first rod flow path 31 is discharged (returned) to the tank 120 via the second rod flow path 32, the first discharge port D1, the first notch flow path 21, the first tank port T1, and the first discharge flow path 135 as shown by arrow V20. Hereinafter, a portion of the working oil guided to the first rod flow path 31 will be referred to as "third working oil," and the remaining portion of the guided working oil will be referred to as "fourth working oil."

[0290] In this way, the third working oil in the working oil guided to the first rod flow path 31 is guided to the tank 120 via the first quick recess 174a instead of through the first notch flow path 21 of the outlet throttle valve column 15. As a result, the flow rate of working oil returning to the tank 120 from the rod end side of the cylinder 114 can be increased, and the working oil can be returned to the tank 120 efficiently from the rod end side.

[0291] By supplying working oil to the cylinder head side of cylinder 114, the working oil returns to the reservoir 120 from the rod end side, and the piston rod 115 is pushed out of cylinder 114 as shown by arrow E5, and the boom 104 (see reference) Figure 1 It was raised.

[0292] As explained above, the independent metering valve 171 of the hydraulic system 170 in the third embodiment is similar to that in the first embodiment, having two independent first inlet throttle valve columns 174 and second inlet throttle valve columns 175 as inlet throttle valve columns.

[0293] Therefore, based on the drive control method of the independent metering valve 171, the hydraulic system 170 and the hydraulic actuator 111 (hydraulic cylinder 113), when raising or lowering the boom 104, the flow rate of the working oil flowing into the rod end side or cylinder head side of the cylinder 114 can be adjusted with high performance, similar to the first embodiment.

[0294] Furthermore, the drive control method of the independent metering valve 171, hydraulic system 170, and hydraulic actuator 111 (hydraulic cylinder 113) in the third embodiment achieves the same effect as in the first embodiment.

[0295] Furthermore, the independent metering valve 171 of the hydraulic system 170 in the third embodiment has a first quick recess 174a in the first inlet throttle valve column 174 and a second quick recess 175a in the second inlet throttle valve column 175.

[0296] Therefore, according to the drive control method of the independent metering valve 171, the hydraulic system 170 and the hydraulic actuator 111 (hydraulic cylinder 113), as described above, the pressure loss of the working oil flowing into the hydraulic cylinder 113 can be reduced and the flow rate of the working oil discharged from the hydraulic cylinder 113 can be increased.

[0297] [Fourth Implementation]

[0298] <Independent Metering Valve>

[0299] Figure 11 This indicates that in the fourth embodiment, an independent metering valve (an example of the control valve in the claims) 181 is used to control the boom 105 (see reference). Figure 1 An illustrative diagram of an example of a hydraulic system (an example of the fluid system of claim 180) held in a stationary state. Figure 11 This is an explanatory diagram that is equivalent to keeping the piston rod 118 of the hydraulic cylinder 116 stationary.

[0300] like Figure 1 , Figure 11 As shown, the independent metering valve 181 of the fourth embodiment is a valve that controls a hydraulic cylinder (an example of the actuator of the claim) 116, which is used to drive the boom 105 of the construction machinery 100.

[0301] Furthermore, the hydraulic cylinder 116 that operates the boom 105 is typically located near the boom 105, but... Figure 1For convenience, hydraulic cylinder 116 is described in the same position as hydraulic cylinder 113 of boom 104.

[0302] like Figure 11 As shown, the hydraulic cylinder 116 includes: a cylinder 117; a piston rod 118 which is disposed within the cylinder 117 in a slidingly movable manner; a cover port Hp which is disposed within the cylinder 117; and a rod port Rp.

[0303] The cylinder head port Hp is located at the cylinder head side 117a of cylinder 117. The piston rod port Rp is located at the piston rod side 117b of cylinder 117.

[0304] The independent metering valve 181 includes a valve body (an example of the module body of the claims) 183, a first inlet throttle valve stem 184, a second inlet throttle valve stem 185, and an outlet throttle valve stem 186. The other structures of the independent metering valve 181 are the same as those of the independent metering valve 171 in the third embodiment.

[0305] The valve body 183 has the same structure as the valve body 173 in the third embodiment, and the same reference numerals as those used for the valve body 173 are used to describe each structure.

[0306] The outlet throttle valve 186 is formed in the same manner as the outlet throttle valve 15 of the first embodiment. Hereinafter, the structural reference numerals of the outlet throttle valve 186 are the same as those of the outlet throttle valve 15 of the first embodiment.

[0307] The first inlet throttle valve stem 184 has a first quick recess (an example of the recess of the claim) 184a instead of the first quick recess 174a of the first inlet throttle valve stem 174 of the third embodiment. The other structures of the first inlet throttle valve stem 184 are the same as those of the first inlet throttle valve stem 174.

[0308] The first quick recess 184a is formed, for example, by a stepped portion that is recessed relative to the first shoulder 184b over the entire circumference. Alternatively, the first quick recess 184a may also be formed by a stepped portion and a notch.

[0309] The first quick-access recess 184a is formed at a position closer to one side than one end of the bridging flow path 30. The first quick-access recess 184a is positioned at the first neutral position of the first inlet throttling valve column 184. Figure 11 When positioned as shown, it is configured between the first rod flow path 31 and the second rod flow path 32.

[0310] Figure 12 This is an explanatory diagram illustrating an example of the operation when the boom 105 is pressed using the hydraulic system 180 according to the fourth embodiment. Figure 12This diagram illustrates the action of the piston rod 118 of hydraulic cylinder 116 being pulled into cylinder 117.

[0311] For example Figure 12 As shown, the first inlet throttle valve column 184 is configured to the first supply position ( Figure 12 When the position shown is such that a portion of the other side of the first quick recess 184a is connected to the bridging flow path 30, a portion of one side of the first quick recess 184a is positioned between the first rod flow path 31 and the second rod flow path 32.

[0312] Therefore, the first quick recess 184a connects the bridging flow path 30 with the first rod flow path 31. Thus, the bridging flow path 30 is connected to the rod end Rp (specifically, the rod end side of the cylinder 117) via the first quick recess 184a, the first rod flow path 31, and the rod-side flow path 133.

[0313] Furthermore, the outlet throttle valve 186 is configured to the second discharge position ( Figure 12 In the state shown (position), the bridging flow path 30 is connected to the second rod flow path 32 via the first notch flow path 21 and the first discharge port D1. The second rod flow path 32 is connected to the rod port Rp via the first rod flow path 31 and the rod-side flow path 133. That is, when the outlet throttle valve column 186 is configured to the second discharge position, the bridging flow path 30 is connected to the rod port Hp (specifically, the rod end side of cylinder 117) via the first notch flow path 21.

[0314] The second inlet throttle valve stem 185 has a second quick recess (an example of another recess in the claim) 185a instead of the second quick recess 175a of the second inlet throttle valve stem 175 in the third embodiment. The other structures of the second inlet throttle valve stem 185 are the same as those of the second inlet throttle valve stem 175. The second quick recess 175a is formed, for example, using a stepped portion recessed relative to the second shoulder 185b over the entire circumference. Alternatively, the second quick recess 185a may also be formed using a stepped portion and a notch, for example.

[0315] The second quick recess 185a is formed at a position on the opposite side of the other end of the bridging flow path 30. The second quick recess 185a is positioned at the second neutral position of the second inlet throttle valve column 185. Figure 11 When it reaches the position shown, it is connected to the fourth tank port T4.

[0316] like Figure 12 As shown, the second inlet throttle valve column 185 is configured at the second supply position ( Figure 12 When the position shown is such that a portion of one side of the second quick recess 185a is positioned between the first cover flow path 33 and the second cover flow path 34, a portion of the other side of the first quick recess 184a is connected to the fourth can port T4.

[0317] Therefore, the second quick recess 185a connects the first cap flow path 33 to the fourth can port T4. Thus, the cap port Hp (specifically, the cylinder head side of cylinder 117) is connected to the can 120 via the cap side flow path 134, the first cap flow path 33, the second quick recess 185a, the fourth can port T4, and the fifth discharge flow path 178.

[0318] Furthermore, the outlet throttle valve 186 is configured to the second discharge position ( Figure 12 In the state shown (the position), the cap port Hp is connected to the second cap flow path 34 via the cap side flow path 134 and the first cap flow path 33. Furthermore, the second cap flow path 34 is connected to the tank 120 via the second discharge port D2, the second notch flow path 22, the second tank port T2, and the second discharge flow path 136. That is, the cap port Rp (specifically, the cylinder head side of cylinder 117) is connected to the tank 120 via the second notch flow path 22 of the outlet throttle valve 186 when the outlet throttle valve 186 is positioned at the second discharge position.

[0319] <Drive control method for hydraulic actuators using independent metering valves and hydraulic systems>

[0320] Next, based on Figure 11 , Figure 12 This describes a method for driving and controlling the hydraulic actuator 111, which is driven by an independent metering valve 181 and a hydraulic system 180.

[0321] First, based on Figure 11 This explains how to use an independent metering valve 181 to control the boom 105 of the construction machinery 100 (refer to...). Figure 1 An example of something remaining stationary.

[0322] like Figure 11 As shown, the first inlet throttle valve 184 is positioned in the first neutral position, thereby blocking the first pump port P1 and the first supply port S1. Furthermore, the second inlet throttle valve 185 is positioned in the second neutral position, thereby blocking the second pump port P2 and the second supply port S2.

[0323] Furthermore, the outlet throttle valve 186 is positioned in the center ( Figure 11 (as shown in the figure), use the outlet throttle valve column 186 to block the first tank port T1 and the first discharge port D1, and block the second tank port T2 and the second discharge port D2.

[0324] In this state, the working oil sprayed from the respective ejection ports of the first pump 110A and the second pump 110B returns to the tank 120 via a return loop (not shown), and the boom 105 (see reference) Figure 1 It is kept at rest.

[0325] Next, based on Figure 12 This section describes an example of using an independent metering valve 181 to press the lever 105.

[0326] like Figure 12 As shown, by moving the first inlet throttle valve column 184 in the direction of arrow A12 to the first supply position, the first pump port P1 is connected to the first supply port S1 by utilizing the first inlet throttle flow path 11.

[0327] Furthermore, by positioning the first inlet throttle valve column 184 in the first supply position, the bridging flow path 30 is connected to the first rod flow path 31 via the first quick recess 184a. As a result, the rod port Rp is connected to the bridging flow path 30 via the first quick recess 184a, the first rod flow path 31, and the rod-side flow path 133.

[0328] Furthermore, by moving the second inlet throttle valve 185 in the direction of arrow A13 to the second supply position, the second pump port P2 is connected to the second supply port S2 via the second inlet throttle flow path 12. As a result, the first pump port P1 and the second pump port P2 are connected to the bridging flow path 30 via the first supply port S1 and the second supply port S2, respectively.

[0329] Furthermore, by positioning the second inlet throttle valve column 6 at the second supply position, the first cap flow path 33 and the fourth can port T4 are connected via the second quick recess 185a. As a result, the cap port Hp is connected to the fourth can port T4 via the second quick recess 185a, the first cap flow path 33, and the cap side flow path 134.

[0330] Furthermore, the outlet throttle valve 186 is moved in the direction of arrow A14 and positioned in the second discharge position. By positioning the outlet throttle valve 186 in the second discharge position, the first notch flow path 21 is connected to the bridging flow path 30, and the first notch flow path 21 is connected to the rod port Rp via the first discharge port D1, etc. Specifically, the rod port Rp is connected to the bridging flow path 30 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133, etc.

[0331] In addition, the outlet throttle valve 186 configured to the second discharge position is used to block the first tank port T1.

[0332] Furthermore, by positioning the outlet throttle valve 186 at the second discharge position, the second discharge port D2 is connected to the second tank port T2 via the second notch flow path 22. As a result, the cap port Hp is connected to the second tank port T2 via the second notch flow path 22, the second discharge port D2, the second cap flow path 34, the first cap flow path 33, and the cap side flow path 134.

[0333] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V21. Furthermore, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V22. Therefore, the working oils ejected from the first pump 110A and the second pump 110B merge in the bridging flow path 30.

[0334] A portion of the combined working oil is guided to the first rod flow path 31 via the first quick recess 184a, as indicated by arrow V23. Furthermore, the remaining portion of the combined working oil is guided to the first rod flow path 31 via the first notch flow path 21, the first discharge port D1, and the second rod flow path 32, as indicated by arrow V24. Hereinafter, the portion of the combined working oil will be referred to as "first working oil," and the remaining portion will be referred to as "second working oil."

[0335] The first and second working oils, guided to the first rod flow path 31, flow into the rod end side of the cylinder 117 via the rod side flow path 133 and the rod port Rp as shown by arrow V25.

[0336] In this way, the first working oil in the bridging flow path 30 is guided to the first rod flow path 31 via the first quick recess 184a instead of through the first notch flow path 21 of the outlet throttle valve column 186. This reduces the pressure loss of the working oil supplied from the bridging flow path 30 to the rod end side of the cylinder 117. That is, working oil can be supplied to the rod end side of the cylinder 117 efficiently.

[0337] On the other hand, the working oil on the cylinder head side in cylinder 117 is guided to the first cover flow path 33 via the cover port Hp and the cover side flow path 134 as shown by arrow V26. A portion of the working oil guided to the first cover flow path 33 is discharged (returned) to the tank 120 via the second quick recess 185a and the fifth discharge flow path 178 as shown by arrow V27.

[0338] Furthermore, the remaining portion of the working oil guided to the first cover flow path 33 is discharged (returned) to the tank 120 via the second cover flow path 34, the second discharge port D2, the second notch flow path 22, the second tank port T2, and the second discharge flow path 136 as shown by arrow V28. Hereinafter, a portion of the working oil guided to the first cover flow path 33 will be referred to as "third working oil", and the remaining portion of the guided working oil will be referred to as "fourth working oil".

[0339] In this way, the third working oil in the working oil guided to the first cover flow path 33 is guided to the tank 120 via the second quick recess 185a instead of through the second notch flow path 22 of the outlet throttle valve column 186. As a result, the flow rate of working oil returning from the cylinder head side of the cylinder 117 to the tank 120 can be increased, and the working oil can be returned to the tank 120 from the cylinder head side efficiently.

[0340] By supplying working oil to the rod end side of cylinder 117, the working oil returns to tank 120 from the cylinder head side, and piston rod 118 is pulled into cylinder 117 as shown by arrow E6, piston rod 105 (see reference) Figure 1 (It was pressed down.)

[0341] As explained above, the independent metering valve 181 of the hydraulic system 180 in the fourth embodiment is similar to that in the first embodiment, having two independent first inlet throttle valve columns 184 and second inlet throttle valve columns 185 as inlet throttle valve columns.

[0342] Therefore, based on the drive control method of the independent metering valve 181, the hydraulic system 180 and the hydraulic actuator 111, when the stick 105 is pressed, the flow rate of the working oil flowing into the stick end side of the cylinder 117 can be adjusted with high performance, similar to the first embodiment.

[0343] Furthermore, the drive control method of the independent metering valve 181, hydraulic system 180, and hydraulic actuator 111 in the fourth embodiment achieves the same effect as in the first embodiment.

[0344] Furthermore, the independent metering valve 181 of the hydraulic system 180 in the fourth embodiment has a first quick recess 184a at the first inlet throttle valve column 184 and a second quick recess at the second inlet throttle valve column 185.

[0345] Therefore, based on the drive control method of the independent metering valve 181, the hydraulic system 180, and the hydraulic actuator 111, as described above, the pressure loss of the working oil flowing into the hydraulic cylinder 116 can be reduced, and the flow rate of the working oil discharged from the hydraulic cylinder 116 can be increased.

[0346] [Fifth Implementation]

[0347] <Independent Metering Valve>

[0348] Figure 13 This indicates that in the fifth embodiment, an independent metering valve (an example of the control valve in the claims) 191 is used to control the boom 105 (see reference). Figure 1 An illustrative diagram of an example of a hydraulic system (an example of the fluid system of claim 190) held in a stationary state. Figure 13 This is an explanatory diagram that is equivalent to keeping the piston rod 118 of the hydraulic cylinder 116 stationary.

[0349] like Figure 1 , Figure 13 As shown, the independent metering valve 191 in the fifth embodiment is a valve that controls the hydraulic cylinder 116, which is used to drive the boom 105 of the construction machinery 100.

[0350] The independent metering valve 191 includes a valve body (an example of the module body of the claims) 193, a first inlet throttle valve stem 194, a second inlet throttle valve stem 195, and an outlet throttle valve stem 196. The other structures of the independent metering valve 191 are the same as those of the independent metering valve 181 of the fourth embodiment.

[0351] The valve body 193 has a bypass flow path 197 with a U-shaped cross-section along the axial direction, a third check valve 198 disposed midway through the bypass flow path 197, and a bypass port G2. The other structures of the valve body 193 are the same as those of the valve body 183 in the fourth embodiment. Hereinafter, the various structures of the valve body 193 will be described using the same reference numerals as those used for the valve body 183 in the fourth embodiment.

[0352] Bypass flow path 197 connects the first notch flow path 21 to bypass port G2 via the third check valve 198. Bypass port G2 is positioned centrally at the outlet throttle valve spool 196. Figure 13 The state configuration (shown in the figure) is located axially inside the third gap flow path 199 discussed later.

[0353] The first inlet throttle valve 194 removes the first quick recess 184a from the first inlet throttle valve 184 of the fourth embodiment, and the first pump port P1 is formed at a position axially closer (outer) than the first supply port S1. The other structures of the first inlet throttle valve 194 are the same as those of the first inlet throttle valve 184.

[0354] The second inlet throttle valve 195 removes the second quick recess 185a from the second inlet throttle valve 185 of the fourth embodiment, and the second pump port P2 is formed at a position on the opposite side (outer side) of the second supply port S2 in the axial direction. The other structures of the second inlet throttle valve 195 are the same as those of the second inlet throttle valve 185.

[0355] A third notch flow path 199 is formed in the outlet throttle valve 196. The other structures of the outlet throttle valve 196 are formed in the same way as those of the outlet throttle valve 186 in the fourth embodiment. Hereinafter, the various structures of the outlet throttle valve 196 will be described using the same reference numerals as those used in the outlet throttle valve 186 of the fourth embodiment.

[0356] The third notch flow path 199 is formed axially inward of the second notch flow path 22. When the outlet throttle valve column 196 is positioned in the central position, the third notch flow path 199 is positioned axially outward of the bypass port G2 and communicates with the connection port G3. The connection port G3 communicates with the other end of the bridging flow path 30.

[0357] Figure 14 This refers to the fifth embodiment, where the hydraulic system 190 is used to pull the boom 105 (see reference). Figure 1 An illustrative diagram illustrating an example of movement during ( ). Figure 14 This diagram illustrates the function of the piston rod 118, which is equivalent to the piston rod 118 that pushes out the hydraulic cylinder 116.

[0358] like Figure 14 As shown, the third notch flow path 199 is configured to the regeneration position at the outlet throttle valve 196. Figure 14 (As shown in the image) When connected to the connection port G3, it is connected to the bypass port G2.

[0359] Figure 15 This is an explanatory diagram illustrating an example of excavation using a hydraulic system 190 to pull the boom 105 according to the fifth embodiment. Figure 15 This diagram illustrates the function of the piston rod 118, which is equivalent to the piston rod 118 that pushes out the hydraulic cylinder 116.

[0360] like Figure 15 As shown, the third notch flow path 199 is configured at the first discharge position at the outlet throttle valve 196. Figure 15 When the position shown is connected to the bypass port G2, it is positioned axially inward of the connection port G3.

[0361] Figure 16 This is an explanatory diagram illustrating an example of the operation when the boom 105 is pressed using the hydraulic system 190 according to the fifth embodiment. Figure 16 This diagram illustrates the action of the piston rod 118 of hydraulic cylinder 116 being pulled into cylinder 117.

[0362] like Figure 16 As shown, the third notch flow path 199 is configured at the second discharge position at the outlet throttle valve column 196. Figure 16 When the position shown is connected to the connection port G3, it is configured to be located axially outward from the bypass port G2.

[0363] <Drive control method for hydraulic actuators using independent metering valves and hydraulic systems>

[0364] Next, based on Figures 13-16 This describes a method for driving and controlling the hydraulic actuator 111, which is driven by an independent metering valve 191 and a hydraulic system 190.

[0365] First, based on Figure 13 This explains how to use an independent metering valve 191 to control the boom 105 of the construction machinery 100 (refer to...). Figure 1 An example of something remaining stationary.

[0366] like Figure 13 As shown, the first inlet throttle valve column 194 is positioned in the first neutral position. Figure 13 The first pump port P1 and the first supply port S1 are blocked by the first inlet throttle valve 194 (as shown in the diagram). Furthermore, the second inlet throttle valve 195 is positioned in the second neutral position (as indicated in the diagram). Figure 13 (as shown in the figure) and the second pump port P2 and the second supply port S2 are blocked by the second inlet throttle valve column 195.

[0367] Furthermore, the outlet throttle valve 196 is positioned in the center to block the first tank port T1 and the first discharge port D1, and the second tank port T2 and the second discharge port D2 are also blocked.

[0368] In this state, the working oil sprayed from the respective ejection ports of the first pump 110A and the second pump 110B returns to the tank 120 via a return loop (not shown), and the boom 105 (see reference) Figure 1 It is kept at rest.

[0369] Next, based on Figure 14 This section describes an example of movement when the boom 105 is pulled using the independent metering valve 191. Furthermore, movement when the boom 105 is pulled refers to movement without using the bucket 106 (see reference). Figure 1 The action of pulling the boom 105 when digging soil, etc.

[0370] like Figure 14 As shown, the first inlet throttle valve 194 is positioned in the first supply position by moving it in the direction of arrow A15. Figure 14 (as shown in the figure), thereby using the first inlet throttling flow path 11 to connect the first pump port P1 with the first supply port S1.

[0371] Furthermore, it is positioned at the second supply position by moving the second inlet throttle valve column 195 in the direction of arrow A16. Figure 14 (as shown in the diagram), thereby connecting the second pump port P2 to the second supply port S2 using the second inlet throttling flow path 12. As a result, the first pump port P1 and the second pump port P2 are connected to the bridging flow path 30 via the first supply port S1 and the second supply port S2, respectively.

[0372] Furthermore, the outlet throttle valve 196 is moved in the direction of arrow A17 to the regeneration position. By positioning the outlet throttle valve 196 in the regeneration position, the second notch flow path 22 is connected to the bridging flow path 30, and the second notch flow path 22 is connected to the cover port Hp via the second discharge port D2, etc. Specifically, the cover port Hp is connected to the bridging flow path 30 via the connection port G3, the second notch flow path 22, the second discharge port D2, the second cover flow path 34, the first cover flow path 33, and the cover side flow path 134, etc.

[0373] Furthermore, by positioning the outlet throttle valve 196 in the regeneration position, the third notch flow path 199 is connected to the second notch flow path 22, and the third notch flow path 199 is connected to the rod port Rp via the bypass port G2, etc. Specifically, the rod port Rp is connected to the second notch flow path 22 via the connection port G3, the third notch flow path 199, the bypass port G2, the bypass flow path 197, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133, etc.

[0374] Furthermore, the outlet throttle valve 196 configured at the regeneration position is used to block the first tank port T1 and the second tank port T2.

[0375] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V30. Furthermore, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V31. Therefore, the working oils ejected from the first pump 110A and the second pump 110B merge in the bridging flow path 30.

[0376] The working oil after merging is guided to the first cover flow path 33 via the second notch flow path 22, the second discharge port D2, and the second cover flow path 34 as shown by arrow V32. The working oil guided to the first cover flow path 33 flows into the cylinder head side of the cylinder 117 via the cover side flow path 134 and the cover port Hp as shown by arrow V33.

[0377] On the other hand, the working oil on the rod end side of cylinder 117 is guided to bypass flow path 197 via rod port Rp, rod side flow path 133, first rod flow path 31, and second rod flow path 32 as shown by arrow V34. The working oil guided to bypass flow path 197 flows into second gap flow path 22 via third check valve 198, bypass port G2, third gap flow path 199, and connection port G3 as shown by arrow V34.

[0378] The working oil guided to the second notch flow path 22 is guided to the first cover flow path 33 via the second discharge port D2 and the second cover flow path 34. The working oil guided to the first cover flow path 33 flows into the cylinder head side of the cylinder 117 via the cover side flow path 134 and the cover port Hp.

[0379] Thus, when the boom 105 is moved, the rod port Rp of the cylinder 117 can be connected to the cover port Hp, allowing the working oil on the rod end side of the cylinder 117 to flow into the cylinder cover side for regeneration.

[0380] By regenerating the working oil on the rod end side, the piston rod 118 can be quickly pushed out of the cylinder 117 with less energy, as shown by arrow E7. This allows for rapid operation of the movement used to pull the boom 105 with less energy, improving the movement of the boom 105 and achieving energy savings.

[0381] Next, based on Figure 15 This section describes an example of excavation using the independent metering valve 191 to pull the boom 105. Furthermore, excavation by pulling the boom 105 refers to simultaneously pulling the boom 105 and using the bucket 106 (see reference). Figure 1 Actions such as digging soil.

[0382] like Figure 15 As shown, similar to the movement example when the boom is traction 105, the first inlet throttle valve 194 and the second inlet throttle valve 195 are held in the first supply position and the second supply position, respectively. In this state, the outlet throttle valve 196 is moved from the regeneration position ( Figure 14 The position shown is moved in the direction of arrow A18 and positioned at the first discharge position. Figure 15 (as shown in the position). Similarly, when the outlet throttle valve 196 is configured to the regeneration position, the second notch flow path 22 is maintained in a state that is connected to the bridging flow path 30 and connected to the cover port Hp via the second discharge port D2, etc.

[0383] Furthermore, by positioning the outlet throttle valve 196 at the first discharge position, the third gap flow path 199 is kept blocked relative to the second discharge port D2.

[0384] Furthermore, by positioning the outlet throttle valve 196 at the first discharge position, the first discharge port D1 and the first tank port T1 are connected by the first notch flow path 21. As a result, the rod port Rp is connected to the first tank port T1 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133.

[0385] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V30. Furthermore, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V31. Therefore, the working oils ejected from the first pump 110A and the second pump 110B merge in the bridging flow path 30.

[0386] The working oil after merging is guided to the first cover flow path 33 via the second notch flow path 22, the second discharge port D2, and the second cover flow path 34 as shown by arrow V32. The working oil guided to the first rod flow path 31 flows into the cylinder head side of the cylinder 117 via the cover side flow path 134 and the cover port Hp as shown by arrow V33.

[0387] On the other hand, the working oil on the rod end side of cylinder 117 is guided to the first discharge port D1 via rod port Rp, rod side flow path 133, first rod flow path 31, and second rod flow path 32 as shown by arrow V35. The working oil guided to the first discharge port D1 is discharged to tank 120 (returning to tank 120) via the first notch flow path 21, first tank port T1, and first discharge flow path 135 as shown by arrow V35.

[0388] Thus, while digging with the bucket 106 while pulling the boom 105, the working oil on the boom end side of the cylinder 117 can be returned to the tank 120 from the boom port Rp.

[0389] Therefore, the piston rod 118 can be pushed out of the cylinder 117 as indicated by arrow E7 using the working oil sprayed from the respective nozzles of the first pump 110A and the second pump 110B. Thus, while digging with the bucket 106 while simultaneously pulling the boom 105, the digging force of the bucket 106 can be ensured, and the digging work of the construction machinery 100 (see reference) can be carried out efficiently. Figure 1 The excavation work was carried out.

[0390] Next, based on Figure 16 This section describes an example of using an independent metering valve 191 to press the lever 105.

[0391] like Figure 16 As shown, similarly to when the boom is traction 105, the first inlet throttle valve 194 and the second inlet throttle valve 195 are held in the first supply position and the second supply position, respectively. In this state, the outlet throttle valve 196 is moved in the direction of arrow A19 and positioned in the second discharge position. Figure 16 (The location shown).

[0392] By positioning the outlet throttle valve 196 at the second discharge position, the first notch flow path 21 is connected to the bridging flow path 30, and the first notch flow path 21 is connected to the rod port Rp via the first discharge port D1, etc. Specifically, the rod port Rp is connected to the bridging flow path 30 via the first notch flow path 21, the first discharge port D1, the second rod flow path 32, the first rod flow path 31, and the rod-side flow path 133, etc.

[0393] Furthermore, the outlet throttle valve 196 configured at the second discharge position is used to block the first tank port T1.

[0394] Furthermore, by positioning the outlet throttle valve 126 at the second discharge position, the second discharge port D2 is connected to the second tank port T2 via the second notch flow path 22. As a result, the cap port Hp is connected to the second tank port T2 via the second notch flow path 22, the second discharge port D2, the second cap flow path 34, the first cap flow path 33, and the cap side flow path 134.

[0395] In this state, the working oil ejected from the nozzle of the first pump 110A is guided to the bridging flow path 30 via the first pump port P1, the first inlet throttling flow path 11, the first supply port S1, and the first check valve 41 as shown by arrow V30. Furthermore, the working oil ejected from the nozzle of the second pump 110B is guided to the bridging flow path 30 via the second pump port P2, the second inlet throttling flow path 12, the second supply port S2, and the second check valve 42 as shown by arrow V31. Therefore, the working oils ejected from the first pump 110A and the second pump 110B merge in the bridging flow path 30.

[0396] The working oil after merging is guided to the first rod flow path 31 via the first notch flow path 21, the first discharge port D1, and the second rod flow path 32 as shown by arrow V36. The working oil guided to the first rod flow path 31 flows into the rod end side of the cylinder 117 via the rod side flow path 133 and the rod port Rp as shown by arrow V36.

[0397] On the other hand, the working oil on the cylinder head side of cylinder 117 is guided to the first cover flow path 33 via cover port Hp and cover side flow path 134 as shown by arrow V37. The working oil guided to the first cover flow path 33 is discharged to tank 120 (returning to tank 120) via the second cover flow path 34, the second discharge port D2, the second notch flow path 22, the second tank port T2, and the second discharge flow path 136 as shown by arrow V37.

[0398] Thus, working oil is supplied to the rod end side of cylinder 117, causing the working oil to return from the cylinder head side to the reservoir 120, thereby pulling the piston rod 118 into cylinder 117 as shown by arrow E8, and the piston rod 105 (see reference) Figure 1 (It was pressed down.)

[0399] As explained above, the independent metering valve 191 of the hydraulic system 190 in the fifth embodiment is similar to that in the fourth embodiment, having two independent first inlet throttle valve columns 194 and second inlet throttle valve columns 195 as inlet throttle valve columns.

[0400] Therefore, based on the drive control method of the independent metering valve 191, the hydraulic system 190, and the hydraulic actuator 111, similar to the first embodiment, the flow rate of the working oil flowing into the cylinder head end side of the cylinder 117 can be adjusted with high performance while moving and digging, while simultaneously pulling the boom 105.

[0401] Furthermore, based on the drive control method of the independent metering valve 191, the hydraulic system 190, and the hydraulic actuator 111, when the boom 105 is pressed, the flow rate of the working oil flowing into the boom end side of the cylinder 117 can be adjusted with high performance, similar to the first embodiment.

[0402] Furthermore, the drive control method for the independent metering valve 191, hydraulic system 190, and hydraulic actuator 111 in the fifth embodiment achieves the same effect as in the first embodiment.

[0403] Furthermore, the scope of protection of the present invention is not limited to the described embodiments, and various modifications can be made without departing from the spirit of the present invention.

[0404] For example, in the above embodiments, the construction machinery 100 was described as an example of a hydraulic excavator, but it is not limited thereto. For example, the present invention can also be applied to construction machinery other than hydraulic excavators, such as hydraulic cranes.

[0405] In the above embodiments, the fluid system has been described as an example of a hydraulic system equipped with a hydraulic control device, but it is not limited to this. For example, the fluid system may also be equipped with a fluid control device other than a hydraulic control device, such as an air pressure control device or a water pressure control device.

[0406] In the above embodiments, hydraulic cylinders 113 and 116 have been described as examples of actuators, but the invention is not limited thereto. The invention can also be applied to actuators such as hydraulic motors.

[0407] In the above embodiments, electromagnetic proportional valves 7, 8, 16, and 17 have been described as examples of solenoid valves, but the invention is not limited thereto. The invention can also be applied to various types of solenoid valves, for example, those driven by electrical signals. Alternatively, the pilot pressure of hydraulic pressure can be used instead of electromagnetic proportional valves 7, 8, 16, and 17 to control the first inlet throttle valve columns 5, 153, 174, 184, and 194, the second inlet throttle valve columns 6, 154, 175, 185, and 195, and the outlet throttle valve columns 15, 186, and 196.

[0408] Furthermore, without departing from the spirit of the present invention, the constituent elements of the above-described embodiments can be replaced with well-known constituent elements. Additionally, the various modifications described above can also be combined.

[0409] For example, in the embodiments described above, hydraulic systems 109, 150, 170, 180, and 190, which use working oil, have been described as fluid systems. However, this is not a limitation; the structure of the embodiments described above can be applied to fluid systems that use a wide variety of fluids. For example, systems that use water or air instead of working oil as the fluid can be cited as examples of fluid systems.

[0410] In the above embodiment, the inlet throttle valve column receiving part, which houses the first inlet throttle valve column 5 and the second inlet throttle valve column 6, has been described using the first valve column hole 10 as an example. However, the structure of the inlet throttle valve column receiving part is not limited to a hole. The inlet throttle valve column receiving part can be constructed to have a space capable of accommodating the first inlet throttle valve column 5 and the second inlet throttle valve column 6.

Claims

1. A control valve comprising: The first inlet throttling valve column has a first inlet throttling flow path connected to the first pump; The second inlet throttle valve column has a second inlet throttle flow path connected to the second pump; A supply flow path, which is connected to the first inlet throttling flow path and the second inlet throttling flow path, and is also connected to the supply and discharge ports of the actuator; and The inlet throttle valve column receiving section houses both the first inlet throttle valve column and the second inlet throttle valve column. The inlet throttle valve column receiving part has a middle part, which is located in the middle of the first inlet throttle valve column and the second inlet throttle valve column in the axial direction of each inlet throttle valve column, and communicates with the tank.

2. The control valve according to claim 1, wherein, The control valve has an outlet throttle valve stem that has a flow path communicating with the supply flow path and the supply / discharge port of the actuator.

3. A control valve comprising: The first inlet throttling valve column has a first inlet throttling flow path connected to the first pump; The second inlet throttle valve column has a second inlet throttle flow path connected to the second pump; A supply flow path, which is connected to the first inlet throttling flow path and the second inlet throttling flow path, and is also connected to the supply and discharge ports of the actuator; and An outlet throttle valve column has a flow path communicating with the supply flow path and the supply / discharge port of the actuator. The first inlet throttle valve column has a recess that connects the supply flow path to the supply / discharge port of the actuator, or connects the supply / discharge port of the actuator to the tank.

4. The control valve according to claim 3, wherein, The second inlet throttle valve column has another recess that connects the supply flow path to the supply / discharge port of the actuator, or connects the supply / discharge port of the actuator to the tank.

5. The control valve according to claim 3 or 4, wherein, The control valve comprises a module that includes the first inlet throttle valve column, the second inlet throttle valve column, and the outlet throttle valve column.

6. A control valve comprising: The first inlet throttling valve column has a first inlet throttling flow path connected to the first pump; The second inlet throttle valve column has a second inlet throttle flow path connected to the second pump; The supply flow path is connected to the first inlet throttling flow path and the second inlet throttling flow path, and is also connected to the supply and discharge ports of the actuator; An outlet throttle valve column having a flow path communicating with the supply flow path and the supply / discharge port of the actuator; The module body includes the first inlet throttle valve, the second inlet throttle valve, and the outlet throttle valve. as well as An inlet throttle valve column receiving section is disposed in the module body, which together houses the first inlet throttle valve column and the second inlet throttle valve column. The inlet throttle valve column receiving part has a middle part, which is located in the middle of the first inlet throttle valve column and the second inlet throttle valve column in the axial direction of each inlet throttle valve column, and communicates with the tank.

7. A control valve comprising: The first inlet throttling valve column has a first inlet throttling flow path connected to the first pump; The second inlet throttle valve column has a second inlet throttle flow path connected to the second pump; The supply flow path is connected to the first inlet throttling flow path and the second inlet throttling flow path, and is also connected to the supply and discharge ports of the actuator; An outlet throttle valve column having a flow path communicating with the supply flow path and the supply / discharge port of the actuator; The module body includes the first inlet throttle valve, the second inlet throttle valve, and the outlet throttle valve. as well as An inlet throttle valve column receiving section is disposed in the module body, which together houses the first inlet throttle valve column and the second inlet throttle valve column. The inlet throttle valve column receiving part has a middle section, which is located at the midpoint between the first inlet throttle valve column and the second inlet throttle valve column in their axial directions, and communicates with the tank. The first inlet throttle valve column has a recess that connects the supply flow path to the supply / discharge port of the actuator, or connects the supply / discharge port of the actuator to the tank. The second inlet throttle valve column has another recess that connects the supply flow path to the supply / discharge port of the actuator, or connects the supply / discharge port of the actuator to the tank.

Images