Multi-control valve

Abstract

Provided is a multi-control valve which can easily form a passage and can be compactly formed. A multi-control valve is provided with: a first valve element group including a bucket valve element, an arm valve element, a boom valve element, a first travel valve element, a second travel valve element, and a rotation valve element; a valve block that forms a loading / unloading-side passage and a travel-side passage and through which the respective valve elements of the first valve element group pass; and a second valve body group including a regeneration valve body and a loading / unloading priority valve body for preferentially flowing to the loading / unloading side passage, wherein the valve bodies are inserted into the valve block in a manner of being parallel to the valve bodies of the first valve body group. The valve elements of the first valve element group are arranged in a row in a predetermined direction in the valve block, and the valve elements of the second valve element group are arranged in a row in a predetermined direction in the valve block, and form a row different from that of the valve elements of the first valve element group.

Description

Technical Field

[0001] The present utility model relates to a multi-control valve through which a plurality of valve cores are inserted. Background Art

[0002] In construction machinery such as excavators, there is a multi-control valve that controls the flow of working fluid to each actuator. As an example of the multi-control valve, for example, there is known an oil pressure control valve device of Patent Document 1. In the oil pressure control valve device, valve cores for controlling the flow of working fluid to each actuator, that is, drive system valve cores, are arranged in a row on a main body block.

[0003] Prior Art Documents:

[0004] Patent Documents:

[0005] Patent Document 1: Japanese Patent Laid-Open No. 11-190044. Summary of the Utility Model

[0006] Problems to be Solved by the Utility Model:

[0007] The multi-control valve is also provided with auxiliary system valve cores in addition to the drive system valve cores. The auxiliary system valve cores are valve cores provided in the multi-control valve in response to various requirements such as energy saving and improvement of operability in construction machinery. Examples of the auxiliary system valve cores include a regeneration valve core, a priority valve core, and an unloading valve core. The auxiliary system valve cores are connected to specific valve cores. Therefore, depending on the position where the auxiliary system valve cores are arranged, the passages formed on the multi-control valve become complicated.

[0008] Therefore, an object of the present utility model is to provide a multi-control valve that can easily form passages and can be formed compactly.

[0009] Means for Solving the Problems:

[0010] The multi-control valve of the present disclosure includes: a first spool group including a bucket spool that controls the flow of working fluid supplied to a bucket cylinder, a boom spool that controls the flow of working fluid supplied to a boom cylinder, an arm spool that controls the flow of working fluid supplied to an arm cylinder, a first travel spool that controls the flow of working fluid supplied to a first travel motor, a second travel spool that controls the flow of working fluid supplied to a second travel motor, and a swing spool that controls the flow of working fluid supplied to a swing motor; a valve block formed with a loading / unloading side passage connecting the bucket spool, the boom spool, the arm spool, and the swing spool and a travel side passage connecting the first travel spool and the second travel spool, and through which the respective spools of the first spool group are inserted in parallel with each other; and a second spool group including a regeneration spool that controls the flow of working fluid supplied from a rod side port to a head side port of the boom cylinder, and a loading / unloading priority spool that causes the working fluid to preferentially flow to the loading / unloading side passage by controlling the flow rate of the working fluid flowing in the travel side passage, and the respective spools are inserted through the valve block in a form parallel to the respective spools of the first spool group; the respective spools of the first spool group are arranged in a row on the valve block in a specified direction, and the respective spools of the second spool group are arranged in a row on the valve block in a specified direction and form a row different from the respective spools of the first spool group.

[0011] According to the present disclosure, since the spools of the drive system that actuate the respective cylinders and motors are arranged in a row, it is possible to easily form the passages. Further, by arranging the spools of the auxiliary system other than the spools of the drive system in a row beside the row of the drive system spools, the multi-control valve can be formed compactly. Therefore, the loadability on the machine can be improved.

[0012] Effect of the utility model:

[0013] According to the present disclosure, the passages can be easily formed and can be formed compactly. Description of the drawings

[0014] Figure 1 is a top view showing the multi-control valve of the present embodiment of the present disclosure;

[0015] Figure 2 is showing Figure 1 the circuit diagram of the hydraulic circuit constituted by the multi-control valve;

[0016] Figure 3 is a cross-sectional view observed after cutting the multi-control valve with a cutting line III-III; Figure 1 the multi-control valve;

[0017] Figure 4 is a cross-sectional view observed after cutting the multi-control valve with a cutting line IV-IV; Figure 1 the multi-control valve;

[0018] Figure 5 It is shown Figure 1 A bottom view of a multi-control valve;

[0019] Figure 6 It is cut along the cutting line VI-VI Figure 1 A cross-sectional view of the multi-control valve observed behind;

[0020] Figure 7 The section is made along the section line VII-VII Figure 6 Cross-sectional view of the multi-control valve as viewed from behind. DETAILED DESCRIPTION

[0021] Hereinafter, the multi-control valve 1 of the embodiment of the present disclosure will be described with reference to the above-mentioned drawings. In addition, the directional concepts used in the following description are only used for the convenience of description, and the structural orientation of the utility model is not limited to the direction. In addition, the multi-control valve 1 described below is only an embodiment of the utility model. Therefore, the utility model is not limited to the embodiment, and additions, deletions, and changes can be made within the scope of the main purpose of the utility model.

[0022] <Multiple control valve>

[0023] like Figure 1 The multi-control valve 1 shown is provided in a construction machine such as an excavator. The construction machine includes a hydraulic cylinder and a hydraulic motor. In this embodiment, the construction machine includes Figure 2 The hydraulic cylinders shown are bucket cylinder 2, arm cylinder 3, boom cylinder 4, and hydraulic motors such as first travel motor 5, second travel motor 6, and swing motor 7. The construction machine is also equipped with an optional actuator (e.g., optional cylinder) 8. The bucket cylinder 2, arm cylinder 3, and boom cylinder 4 respectively operate the bucket, arm, and boom (none of which are shown). The first travel motor 5 and the second travel motor 6 respectively operate a pair of crawlers. The optional cylinder 8 operates, for example, a circuit breaker and a joint (NIPPLA).

[0024] The multi-control valve 1 is connected to a plurality of actuators 2 to 8. The multi-control valve 1 controls the flow of the working fluid supplied to and discharged from the plurality of actuators 2 to 8. In addition, the multi-control valve 1 is a multi-control valve of a single pump system having one pump port 35 as described later in the present embodiment. The multi-control valve 1 mainly includes a valve block 11, a first valve core group 12, and a second valve core group 13.

[0025] The valve block 11 has various passages 21a to 27a, 21b to 27b, 32, 33, 34, 36 and ports 35, 36a, which will be described in detail later. Figure 1The valve block 11 is formed in a rectangular shape when viewed from the top in the height direction. In addition, a side surface (i.e., one side surface) of the valve block 11 located on one side in the short side direction is formed. Figure 2 The pump port 35 and the tank port 36a are shown. Each port 35 and 36a is connected to the hydraulic pump 16 and the tank 17. In addition, a plurality of actuator ports (not shown) are formed on the side surface (i.e., the other side surface) located on the other side in the short side direction of the valve block 11. Each actuator port is connected to a plurality of actuators 2 to 8.

[0026] The first valve core group 12 is as follows Figure 1 The valve cores 21 to 27 of multiple driving systems are shown. In more detail, the first valve core group 12 includes a first travel valve core 21, a second travel valve core 22, a bucket valve core 23, a boom valve core 24, an arm valve core 25, a rotation valve core 26 and an optional valve core 27. On the other hand, the second valve core group 13 includes valve cores 28, 29 and a valve body 30 for multiple auxiliary systems. In more detail, the second valve core group 13 includes a loading and unloading priority valve core (hereinafter referred to as "loading and unloading priority valve core") 28 with unloading function, a boom regeneration valve core 29, and a pressure compensation valve body 30.

[0027] Each valve core 21 to 29 and valve body 30 are slidably inserted through valve block 11. Valve cores 21 to 27 of the drive system control the flow of working fluid to each actuator 2 to 8 by changing their positions. On the other hand, valve cores 28 and 29 of the auxiliary system and valve body 30 for pressure compensation realize various functions (regeneration function, loading and unloading priority function, unloading function and pressure holding function) by changing their positions.

[0028] Again, the multi-control valve 1 is as Figure 1 and Figure 3 As shown, there are a plurality of solenoid valves 14a to 14r and a plurality of relief valves 15a to 15h. Each solenoid valve 14a to 14r is provided on the valve block 11 corresponding to each valve core 21 to 29. Each solenoid valve 14a to 14r outputs a pilot pressure corresponding to an input signal to the corresponding valve core 21 to 29. Thus, each solenoid valve 14a to 14r changes the position of the corresponding valve core 21 to 29, that is, strokes the corresponding valve core 21 to 29. In addition, as described in detail later, the plurality of solenoid valves 14a to 14r respectively constitute two solenoid valve groups 14A and 14B.

[0029] Figure 1 , Figure 4 and Figure 5The multiple relief valves 15a to 15h shown are respectively provided in the valve block 11 corresponding to a part of the spools 21 to 27 of the drive system, namely, the spools 23 to 25 and 27. When the working fluid supplied from the corresponding spools 23 to 25 and 27 to the actuators 2 to 4 and 8 becomes equal to or higher than a specified relief pressure, each of the relief valves 15a to 15h discharges the working fluid to the tank 17. As will be described in detail later, the multiple relief valves 15a to 15h respectively constitute a first relief valve group 15A and a second relief valve group 15B.

[0030] <Hydraulic Circuit in the Multi-Control Valve>

[0031] Hereinafter, with reference to Figure 2 the hydraulic circuit 9 in the multi-control valve 1 will be described. Various passages such as a loading / unloading side passage 32, a traveling side passage 33, and a communication passage 34 are mainly formed on the valve block 11. The loading / unloading side passage 32 is connected to the pump port 35. The pump port 35 is connected to a hydraulic pump 16 that discharges the working fluid. The loading / unloading system spools 23 to 27 among the spools 21 to 27 of the drive system are connected to the loading / unloading side passage 32 in a side-by-side manner. The loading / unloading system spools 23 to 27 are spools that control the working fluid flowing in the loading / unloading system actuators 2 to 4, 7, and 8. In the present embodiment, the loading / unloading system actuators 2 to 4, 7, and 8 are a bucket cylinder 2, an arm cylinder 3, a boom cylinder 4, a swing motor 7, and a selective cylinder 8. That is, the loading / unloading system spools 23 to 27 include a bucket spool 23, an arm spool 24, a boom spool 25, a swing spool 26, and a selective spool 27.

[0032] The bucket spool 23 controls the flow of the working fluid supplied to the bucket cylinder 2. More specifically, the bucket spool 23 is connected to the loading / unloading side passage 32 and the tank passage 36. The tank passage 36 extends in the long side direction in the valve block 11 and is formed throughout the valve block 11 (refer to Figure 3 described in detail later). Moreover, as Figure 2 shown, the tank passage 36 is connected to the tank 17 via a tank port 36a. In addition, the bucket spool 23 is connected to the head side port 2a of the bucket cylinder 2 via a head side passage 23a and is connected to the rod side port 2b of the bucket cylinder 2 via a rod side passage 23b. Further, the bucket spool 23 is pressed in a direction opposite to the pilot pressure output from each of the solenoid valves 14e and 14f. Also, the bucket spool 23 is biased by a spring mechanism 43 in a form that opposes the applied pilot pressure. Therefore, the bucket spool 23 strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14e and 14f. The bucket spool 23 switches the connection destinations of the loading / unloading side passage 32 and the tank passage 36 by stroking, and also adjusts the opening degree of the bucket spool 23. Thereby, the bucket spool 23 controls the flow of the working fluid with respect to the head side port 2a and the rod side port 2b of the bucket cylinder 2.

[0033] The spool 24 for the dipper controls the flow of the working fluid supplied to the dipper cylinder 3. More specifically, the spool 24 for the dipper has a first spool member 24c and a second spool member 24d. The first spool member 24c and the second spool member 24d are respectively connected to the loading and unloading side passage 32 and the tank passage 36. Also, the first spool member 24c and the second spool member 24d are connected to the head side port 3a of the dipper cylinder 3 via the head side passage 24a. Also, the first spool member 24c is connected to the rod side port 3b via the rod side passage 24b. In addition, the first spool member 24c is pressed in a direction opposing the pilot pressure output from each of the solenoid valves 14g, 14h. Also, the second spool member 24d is pressed in a form opposing the pilot pressure output from each of the solenoid valves 14h, 14i. In addition, spring mechanisms 44, 45 that apply a force opposing the pressed pilot pressure are respectively provided on the first spool member 24c and the second spool member 24d. Therefore, the first spool member 24c strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14g, 14h, and the second spool member 24d strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14h, 14i. The first spool member 24c and the second spool member 24d switch the connection destinations of the loading and unloading side passage 32 and the tank passage 36 by stroking, and also respectively adjust the opening degrees of the first spool member 24c and the second spool member 24d. Thereby, the spool 24 for the dipper controls the flow of the working fluid with respect to the head side port 3a and the rod side port 3b of the dipper cylinder 3.

[0034] The boom spool 25 controls the flow of the working fluid supplied to the boom cylinder 4. More specifically, the boom spool 25 has a first spool member 25c and a second spool member 25d. The first spool member 25c and the second spool member 25d are respectively connected to the handling side passage 32 and the tank passage 36. In addition, the first spool member 25c is connected to the rod side port 4b via the rod side passage 25b. Also, the first spool member 25c is pressed in a direction opposite to the pilot pressure output from each of the solenoid valves 14j, 14k. The second spool member 25d is connected to the head side port 4a of the boom cylinder 4 via the head side passage 25a. Also, the second spool member 25d is pressed in a direction opposite to the pilot pressure output from each of the solenoid valves 14k, 14l. In addition, spring mechanisms 46, 47 that apply a force to oppose the applied pilot pressure are provided on the first spool member 25c and the second spool member 25d. Therefore, the first spool member 25c strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14j, 14k, and the second spool member 25d strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14k, 14l. The first spool member 25c and the second spool member 25d switch the connection destinations of the handling side passage 32 and the tank passage 36 by stroking, and also adjust the opening degrees of the first spool member 25c and the second spool member 25d, respectively. Thereby, the boom spool 25 controls the flow of the working fluid relative to the head side port 4a and the rod side port 4b of the boom cylinder 4.

[0035] The swing spool 26 controls the flow of the working fluid supplied to the swing motor 7. More specifically, the swing spool 26 is connected to the handling side passage 32 and the tank passage 36. In addition, the swing spool 26 is respectively connected to the first supply / discharge port 7a and the second supply / discharge port 7b of the swing motor 7 via the supply / discharge passages 26a, 26b. Also, the swing spool 26 is pressed in a direction opposite to the pilot pressure output from each of the solenoid valves 14m, 14n. Also, the swing spool 26 is biased by a spring mechanism 48 in a form that opposes the applied pilot pressure. Therefore, the swing spool 26 strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14m, 14n. The swing spool 26 switches the connection destinations of the handling side passage 32 and the tank passage 36 by stroking, and also adjusts the opening degree of the swing spool 26. Thereby, the swing spool 26 controls the flow of the working fluid relative to the first supply / discharge port 7a and the second supply / discharge port 7b of the swing motor 7.

[0036] The flow of the working fluid supplied to the selectable cylinder 8 can be controlled by the selectable spool valve 27. More specifically, the selectable spool valve 27 is connected to the loading / unloading side passage 32 and the tank passage 36. In addition, the selectable spool valve 27 is connected to the head side port 8a of the selectable cylinder 8 via the head side passage 27a and to the rod side port 8b via the rod side passage 27b. Also, the selectable spool valve 27 is pressured in a direction opposite to the pilot pressure output from each of the electromagnetic valves 14o, 14p. Further, the selectable spool valve 27 is urged by the spring mechanism 49 in a form that opposes the pressured pilot pressure. Therefore, the selectable spool valve 27 strokes to a position corresponding to the pilot pressure of each of the electromagnetic valves 14o, 14p. The selectable spool valve 27 switches the connection destinations of the loading / unloading side passage 32 and the tank passage 36 by stroking and also adjusts the opening degree of the selectable spool valve 27. Thereby, the selectable spool valve 27 controls the flow of the working fluid with respect to the head side port 8a and the rod side port 8b of the selectable cylinder 8.

[0037] The traveling side passage 33 is connected to the loading / unloading side passage 32 via the loading / unloading priority spool valve 28 described in detail later. The working fluid of the hydraulic pump 16 is introduced into the traveling side passage 33 via the loading / unloading priority spool valve 28. Also, the traveling side passage 33 is connected in a form where the traveling system spool valves 21, 22 among the spool valves 21 - 27 of the drive system are arranged in parallel. The traveling system spool valves 21, 22 are spool valves that control the flow of the working fluid supplied to the traveling system actuators 5, 6, which are the first traveling motor 5 and the second traveling motor 6.

[0038] One of the traveling system spool valves 21, that is, the first traveling spool valve 21 controls the flow of the working fluid supplied to the first traveling motor 5. More specifically, the first traveling spool valve 21 is connected to the traveling side passage 33 and the tank passage 36. The first traveling spool valve 21 is respectively connected to the first supply / discharge port 5a and the second supply / discharge port 5b of the first traveling motor 5 via the supply / discharge passages 21a, 21b. The first traveling spool valve 21 is pressured in a direction opposite to the pilot pressure output from each of the electromagnetic valves 14a, 14b. Also, the first traveling spool valve 21 is urged by the spring mechanism 41 in a form that opposes the pressured pilot pressure. Therefore, the first traveling spool valve 21 strokes to a position corresponding to the pilot pressure of each of the electromagnetic valves 14a, 14b. The first traveling spool valve 21 switches the connection destinations of the traveling side passage 33 and the tank passage 36 by stroking and also adjusts the opening degree of the first traveling spool valve 21. Thereby, the first traveling spool valve 21 controls the flow of the working fluid with respect to the first supply / discharge port 5a and the second supply / discharge port 5b of the first traveling motor 5.

[0039] The spool 22 of the traveling system of the other party, that is, the second traveling spool 22, controls the flow of the working fluid supplied to the second traveling motor 6. More specifically, the second traveling spool 22 is connected to the traveling side passage 33 and the tank passage 36. The second traveling spool 22 is respectively connected to the first supply / discharge port 6a and the second supply / discharge port 6b of the second traveling motor 6 via the supply / discharge passages 22a and 22b. The second traveling spool 22 is pressed in a direction opposite to the pilot pressure output from each of the solenoid valves 14c and 14d. Also, the second traveling spool 22 is urged by the spring mechanism 42 in a form that opposes the applied pilot pressure. Therefore, the second traveling spool 22 strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14c and 14d. The second traveling spool 22 switches the connection destination of the traveling side passage 33 and the tank passage 36 by stroking, and also adjusts the opening degree of the second traveling spool 22 to the opening degree. Thereby, the second traveling spool 22 controls the flow of the working fluid with respect to the first supply / discharge port 6a and the second supply / discharge port 6b of the second traveling motor 6.

[0040] The communication passage 34 is connected to the first traveling spool 21 and the second traveling spool 22. Moreover, when the communication passage 34 supplies the working fluid to the first traveling motor 5 and the second traveling motor 6, it connects the first traveling motor 5 and the second traveling motor 6. More specifically, when the first traveling spool 21 strokes, the supply / discharge passages 21a and 21b connecting the first traveling motor 5 and the traveling side passage 33 are connected to the communication passage 34. Also, when the second traveling spool 22 strokes, the supply / discharge passages 22a and 22b connecting the second traveling motor 6 and the traveling side passage 33 are connected to the communication passage 34. Thereby, during straight traveling, it is possible to suppress a deviation in the flow rate of the working fluid supplied to the two traveling motors 5 and 6 when the first traveling motor 5 and the second traveling motor 6 operate simultaneously. Therefore, the straight traveling performance of the construction machinery can be improved.

[0041] The loading / unloading priority spool 28 causes the working fluid to flow preferentially to the loading / unloading side passage 32 by controlling the flow rate of the working fluid flowing in the traveling side passage 33. More specifically, the loading / unloading priority spool 28 is connected to the loading / unloading side passage 32 and the traveling side passage 33. The loading / unloading priority spool 28 receives the pilot pressure from the solenoid valve 14q. In addition, the loading / unloading priority spool 28 is urged by the spring mechanism 50 in a form that opposes the applied pilot pressure. Therefore, the loading / unloading priority spool 28 strokes to a position corresponding to the pilot pressure of each of the solenoid valves 14q, and adjusts the opening degree of the loading / unloading priority spool 28. Thereby, the loading / unloading priority spool 28 controls the flow rate of the working fluid flowing in the traveling side passage 33 and causes the working fluid to flow preferentially to the loading / unloading side passage 32.

[0042] Further, the spool valve 28 for loading and unloading has a unloading function. More specifically, the spool valve 28 for loading and unloading can move to the unloading position A1. At the unloading position A1, the working fluid flowing in the loading and unloading side passage 32 is discharged. More specifically, the spool valve 28 for loading and unloading is also connected to the tank passage 36. Moreover, the spool valve 28 for loading and unloading is located at the unloading position A1 when the pilot pressure from the solenoid valve 14q is less than the specified pressure. The spool valve 28 for loading and unloading connects the loading and unloading side passage 32 with the traveling side passage 33 and the tank passage 36 at the unloading position A1. Thereby, the loading and unloading side passage 32 is connected to the tank passage 36 and the hydraulic pump 16 is in the unloading state.

[0043] Further, when the pilot pressure from the solenoid valve 14q is equal to or higher than the specified pressure, the spool valve 28 for loading and unloading is located at the traveling position A2 or the priority position A3. At the traveling position A2 and the priority position A3, the loading and unloading side passage 32 is connected to the traveling side passage 33. Moreover, the working fluid flowing in the loading and unloading side passage 32 is introduced into the traveling side passage 33. On the other hand, the connection between the loading and unloading side passage 32 and the tank passage 36 is cut off. At the traveling position A2, the opening degree of the spool valve 28 for loading and unloading is the maximum opening degree (including full opening). At the priority position A3, the opening degree of the spool valve 28 for loading and unloading (i.e., the opening degree between the loading and unloading side passage 32 and the traveling side passage 33) is adjusted according to the position corresponding to the pilot pressure of each solenoid valve 14q. That is, at the priority position A3, the opening degree of the spool valve 28 for loading and unloading is reduced according to the stroke amount of the spool valve 28 for loading and unloading.

[0044] The boom regeneration spool valve 29 controls the flow of the working fluid supplied from the rod side port 3b of the boom cylinder 3 to the head side port 3a. That is, the boom regeneration spool valve 29 regenerates the working fluid discharged from the rod side port 3b at the head side port 3a. More specifically, the boom regeneration spool valve 29 is connected to the head side passage 24a and the rod side passage 24b connected to the boom cylinder 3. The boom regeneration spool valve 29 receives the pilot pressure from the solenoid valve 14r. In addition, the boom regeneration spool valve 29 is biased by the spring mechanism 51 in a form that opposes the applied pilot pressure. Therefore, the boom regeneration spool valve 29 connects the head side passage 24a and the rod side passage 24b according to the pilot pressure of each solenoid valve 14r. Thereby, the boom regeneration spool valve 29 can regenerate the working fluid discharged from the rod side port 3b at the head side port 3a.

[0045] The pressure compensation valve body 30 maintains the pressure of the loading and unloading side passage 32 by discharging the working fluid. More specifically, the pressure compensation valve body 30 is connected to the loading and unloading side passage 32. The pressure compensation valve body 30 connects the loading and unloading side passage 32 and the tank passage 36 according to the pressure of the loading and unloading side passage 32.

[0046] A plurality of relief valves 15a to 15h are provided corresponding to each of the cylinders 2 to 4, 8. Moreover, when the pressure of the working fluid supplied to the corresponding cylinders 2 to 4, 8 exceeds a specified relief pressure, the plurality of relief valves 15a to 15h discharge the working fluid to the tank 17. More specifically, the relief valves 15a, 15c, 15e, 15g are respectively connected to the head-side passages 23a to 25a, 27a. Also, the relief valves 15b, 15d, 15f, 15h are respectively connected to the rod-side passages 23b to 25b, 27b. In addition, each of the relief valves 15a to 15h is connected to the tank passage 36. When the pressure in the connected passages 23a to 25a, 27a, 23b to 25b, 27b exceeds the specified relief pressure, each of the relief valves 15a to 15h discharges the working fluid to the tank 17.

[0047] <Flow of Working Fluid in Multi-Control Valve>

[0048] When the traveling system actuators 5, 6 are driven, the multi-control valve 1 operates as follows. That is, when pilot pressure is output from any one of the solenoid valves 14a to 14d, the corresponding traveling spools 21, 22 operate. At this time, the loading / unloading priority spool 28 moves to the traveling position A2 by the pilot pressure from the solenoid valve 14q. For example, when pilot pressure is output from the solenoid valves 14a, 14c, the loading / unloading priority spool 28 moves to the traveling position A2 by the pilot pressure from the solenoid valve 14q and the traveling spools 21, 22 operate. As a result, the working fluid from the hydraulic pump 16 is supplied to each of the traveling motors 5, 6. Moreover, each of the traveling motors 5, 6 rotates in the direction in which the construction machine advances. At this time, the two traveling motors 5, 6 are connected by the communication passage 34. As a result, the flow rate deviation of the working fluid supplied to the two traveling motors 5, 6 is suppressed, so the straight running performance of the construction machine can be improved.

[0049] Also, when the loading / unloading system actuators 2 to 4, 7, 8 are driven, it operates as follows. That is, when pilot pressure is output from any one of the solenoid valves 14e to 14n, the corresponding spools 23 to 27 operate. At this time, the loading / unloading priority spool 28 moves to the traveling position A2 by the pilot pressure from the solenoid valve 14q. For example, when pilot pressure is output from the solenoid valve 14e, the bucket spool 23 operates. At the same time, the loading / unloading priority spool 28 moves to the traveling position A2 by the pilot pressure from the solenoid valve 14q, and the opening degree of the loading / unloading priority spool 28 is adjusted to the minimum opening degree (including fully closed). Then, the working fluid from the hydraulic pump 16 is preferentially supplied to the head-side port 2a of the bucket cylinder 2, and the working fluid is also pressed out from the rod-side port 2b and discharged to the tank 17. As a result, the bucket cylinder 2 extends.

[0050] Further, when pilot pressure is output from the solenoid valves 14g and 14i, the boom spool 24 operates. At the same time, the handling priority spool 28 is moved to the traveling position A2 by the pilot pressure from the solenoid valve 14q, and the opening degree of the handling priority spool 28 is adjusted to the minimum opening degree (including fully closed). Then, the working fluid from the hydraulic pump 16 is supplied to the head side port 3a of the boom cylinder 3, and the working fluid is discharged from the rod side port 2b. At this time, by operating the boom regeneration spool 29, the working fluid discharged from the rod side port 2b can be regenerated at the head side port 3a.

[0051] In addition, when the traveling system actuators 5 and 6 and the handling system actuators 2 to 4, 7, and 8 are operated simultaneously, the following operations are performed. That is, pilot pressure is output from any one of the solenoid valves 14a to 14d, and when pilot pressure is output from any one of the solenoid valves 14e to 14n, the corresponding spools 21 to 27 operate. At this time, the handling priority spool 28 is moved to the priority position A3 by the pilot pressure from the solenoid valve 14q. Moreover, the pilot pressure corresponding to the pilot pressure of each of the solenoid valves 14a to 14n is output from the solenoid valve 14q and the opening degree of the handling priority spool 28 is adjusted. More specifically, the opening degree of the handling priority spool 28 is adjusted according to the operation amounts of the respective actuators 2 to 8 (more specifically, the opening degree is reduced). Thereby, the flow rate of the working fluid flowing in the traveling side passage 33 is restricted, and the working fluid preferentially flows into the handling side passage 32. That is, when the traveling system actuators 5 and 6 and the handling system actuators 2 to 4, 7, and 8 are operated simultaneously, the working fluid can preferentially flow to the handling system actuators 2 to 4, 7, and 8.

[0052] In addition, in the multi-control valve 1, when none of the traveling system actuators 5 and 6 and the handling system actuators 2 to 4, 7, and 8 are operated, the following operations are performed. That is, the handling priority spool 28 is located at the unloading position A1. Thereby, the handling side passage 32 is connected to the tank 17 via the handling priority spool 28. Thereby, the hydraulic pump 16 can be brought into an unloading state.

[0053] <Specific Structure of Multi-Control Valve>

[0054] Hereinafter, the specific structure of the multi-control valve 1 will be described. As described above, the valve block 11 of the multi-control valve 1 is formed in a substantially rectangular parallelepiped shape, for example. More specifically, the valve block 11 includes a block main body 11a, a first solenoid valve block 11b, and a second solenoid valve block 11c (refer to Figure 1 and Figure 5 ). Moreover, the respective spools 21 to 29 of the first spool group 12 and the second spool group 13 and the pressure compensation valve body 30 are inserted through the valve block 11 (the block main body 11a in the present embodiment).

[0055] The block body 11a is formed in a substantially rectangular parallelepiped shape, for example. The block body 11a is formed in a rectangular shape when viewed from the top side in the height direction. The valve cores 21 to 29 of the first valve core group 12 and the second valve core group 13 and the pressure compensation valve body 30 are inserted through the block body 11a as follows. That is, the valve cores 21 to 27 of the first valve core group 12 are inserted into the block body 11a as follows. Figure 1 As shown in FIG. 1 , the block bodies 11a are inserted in parallel to each other in a long side direction as an example of a predetermined direction when viewed from above (see also FIG. 1 ). Figure 3 ).Other, Figure 1 In the embodiment, the spring mechanisms 41 to 44, 46, 48, 49 provided at one end of the axial direction (i.e., the height direction) of each valve core 21 to 27 are arranged in a row along the long side direction. In the present embodiment, the valve cores 21 to 27 of the first valve core group 12 are arranged in the order of, for example, the arm valve core 24, the first travel valve core 21, the rotation valve core 26, the boom valve core 25, the optional valve core 27, the second travel valve core 22 and the bucket valve core 23 from one side in the long side direction. In addition, the order in which the valve cores 21 to 27 are arranged in the long side direction is an example, and may be an order different from the above. In the present embodiment, the valve cores 21 to 27 of the first valve core group 12 are arranged in a row and inserted in the central part in the short side direction in the block body 11a.

[0056] The valve cores 28, 29 of the second valve core group 13 and the pressure compensation valve body 30 are as shown in FIG. Figure 1 As shown, the block bodies 11a are inserted in a row along the long side direction as an example of a predetermined direction in a plan view (see also Figure 4 ). In addition, the valve cores 28, 29 and the pressure compensation valve body 30 of the second valve core group 13 are inserted through the block body 11a in a manner different from the valve cores 21 to 27 of the first valve core group 12. In more detail, the second valve core group 13 is as follows: Figure 1 As shown, the valve cores 28, 29 and the pressure compensation valve body 30 of the second valve core group 13 are arranged on the short side of the first valve core group 12 in the block body 11a. That is, the valve cores 28, 29 and the pressure compensation valve body 30 of the second valve core group 13 are inserted through the block body 11a in the form of a row on the short side of the valve cores 21 to 27 of the first valve core group 12. In this embodiment, the valve cores 28, 29 and the pressure compensation valve body 30 are arranged in the order of the arm regeneration valve core 29, the pressure compensation valve body 30 and the loading and unloading priority valve core 28 from the long side.

[0057] The relief valves 15a to 15h are arranged in the block body 11a as follows. Specifically, the relief valves 15b, 15d, 15e, and 15h of the relief valves 15a to 15h constitute a first relief valve group 15A. The rod-side relief valves 15a, 15c, 15f, and 15g of the relief valves 15a to 15h constitute a second relief valve group 15B.

[0058] The first overflow valve group 15A is arranged in a row on the main surface 11d on one side in the height direction in the block body 11a as shown in Figure 1 . Also, the first overflow valve group 15A is arranged in the block body 11a in a form that forms different columns from the first spool group 12 and the second spool group 13 respectively when viewed from above. More specifically, as shown in Figure 1 , the first overflow valve group 15A is arranged in the block body 11a on the other side in the short side direction of the first spool group 12. That is, the overflow valves 15b, 15d, 15e, 15h of the first overflow valve group 15A are arranged in the block body 11a in a form that forms a column on the other side in the short side direction of each spool 21-27 of the first spool group 12.

[0059] On the other hand, as shown in Figure 5 when viewed from below, the second overflow valve group 15B is arranged on one side and the other side in the short side direction of the bottom surface 11f on the other side in the height direction in the block body 11a. More specifically, the overflow valves 15a, 15c of the second overflow valve group 15B are arranged separately on both sides in the long side direction on one side in the short side direction of the bottom surface 11f. Also, the overflow valves 15f, 15g are arranged in the middle part in the long side direction on the other side in the short side direction of the bottom surface 11f. In the present embodiment, the overflow valves 15f, 15g are arranged between the overflow valves 15a, 15c when viewed from the side in the short side direction.

[0060] The first solenoid valve block 11b is a block for mounting the first solenoid valve group 14A as shown in Figure 1 . In addition, the first solenoid valve group 14A includes a plurality of solenoid valves 14a, 14c, 14e, 14g, 14h, 14j, 14k, 14m, 14o, 14q, 14r. The other solenoid valves 14b, 14d, 14f, 14i, 14l, 14n, 14p constitute the second solenoid valve group 14B. The first solenoid valve block 11b is formed, for example, in a prismatic shape extending along the long side direction. The first solenoid valve block 11b is provided on one side surface of the block body 11a on the side in the short side direction as shown in Figure 1 when viewed from above. In the present embodiment, the first solenoid valve block 11b is mounted on one side surface of the block body 11a and a part on one side in the height direction.

[0061] The first solenoid valve group 14A is arranged in a row on the main surface 11e on one side in the height direction of the first solenoid valve block 11b. More specifically, in the first solenoid valve group 14A, a plurality of solenoid valves 14a, 14c, 14e, 14g, 14h, 14j, 14k, 14m, 14o, 14q, 14r are arranged in multiple columns (two columns in the present embodiment). Moreover, each column extends along the long side direction. Therefore, the first solenoid valve group 14A is arranged in multiple columns along the long side direction in the valve block 11 and is arranged to form different columns from the first spool group 12 and the second spool group 13.

[0062] Figure 5 The second solenoid valve block 11c shown is a block for mounting the second solenoid valve group 14B. The second solenoid valve block 11c is, for example, a long-sized member extending in the long side direction. The second solenoid valve block 11c is provided on the bottom surface 11f of the block main body 11a in a bottom view. More specifically, the second solenoid valve block 11c is mounted on the bottom surface 11f of the block main body 11a and at the middle part in the short side direction. In the present embodiment, the second solenoid valve block 11c is arranged corresponding to the first spool group 12 (more specifically, overlapping the first spool group 12 in a bottom view). Moreover, the spring mechanisms 45 and 47 of the stick spool 24 and the boom spool 25 project from the second solenoid valve block 11c toward the other side in the height direction. Thus, in the second solenoid valve block 11c, the spring mechanisms 45 and 47 of the stick spool 24 and the boom spool 25 are arranged in a line at the middle part in the short side direction. Also, the respective relief valves 15a, 15c, 15f, and 15g of the second relief valve group 15B are respectively arranged on one side and the other side in the short side direction with the second solenoid valve block 11c therebetween.

[0063] The second solenoid valve group 14B is arranged in the second solenoid valve block 11c. In the present embodiment, the respective solenoid valves 14b, 14d, 14f, 14i, 14l, 14n, and 14p of the second solenoid valve group 14B are arranged in a line at the middle part in the short side direction together with the spring mechanisms 45 and 47 of the stick spool 24 and the boom spool 25.

[0064] Also, in the valve block 11 (in the present embodiment, the block main body 11a), the respective passages 32, 33, and 34 are formed as follows. That is, the loading / unloading side passage 32, the traveling side passage 33, and the communication passage 34 are formed in the short side direction between the first spool group 12 and the second spool group 13 (see Figure 1 the cutting line V-V and Figure 6 ). Also, the loading / unloading side passage 32, the traveling side passage 33, and the communication passage 34 extend in the long side direction as Figure 6 shown. More specifically, the loading / unloading side passage 32, the traveling side passage 33, and the communication passage 34 penetrate from one end to the other end of the block main body 11a in the long side direction. Moreover, both ends of the loading / unloading side passage 32, the traveling side passage 33, and the communication passage 34 are closed by plugs 60 or plates 66, respectively. In addition, the respective passages 32, 33, and 34 are arranged in the order of the communication passage 34, the traveling side passage 33, and the loading / unloading side passage 34 from one side in the height direction. However, the arrangement order of the respective passages 32, 33, and 34 is not limited to the foregoing order.

[0065] In addition, as Figure 7As shown, on one side surface of the block body 11a, as described above, a pump port 35 is formed. In the present embodiment, the pump port 35 is formed at the middle part in the long side direction. Moreover, the pump port 35 is arranged in a form adjacent to the loading / unloading priority spool 28 in the long side direction. The pump port 35 is connected to the loading / unloading side passage 32. Also, the loading / unloading side passage 32 is configured in the valve block 11 (in the present embodiment, the block body 11a) as follows. That is, the loading / unloading side passage 32 is connected to five branch passages 32a to 32e. Each of the branch passages 32a to 32e is connected to each of the spools 23 to 27 via each check valve 61 to 65. Also, the loading / unloading side passage 32 is connected to the loading / unloading priority spool 28 at the middle part in the long side direction (in the present embodiment, the central part in the length direction). Moreover, the loading / unloading side passage 32 is also as Figure 4 shown connected to the traveling side passage 33 and the tank passage 36 via the loading / unloading priority spool 28. In addition, the loading / unloading side passage 32 is as Figure 2 and 4 shown connected to the pressure compensation valve body 30.

[0066] The traveling side passage 33 is also as Figure 4 shown connected to the loading / unloading priority spool 28 at the middle part in the long side direction (in the present embodiment, the central part in the length direction). In addition, the traveling side passage 33 is as Figure 6 shown connected to the first traveling spool 21 and the second traveling spool 22. The first traveling spool 21 and the second traveling spool 22 are arranged separated from each other in the long side direction on the traveling side passage 33. Moreover, the loading / unloading priority spool 28 is as Figure 7 shown arranged between the first traveling spool 21 and the second traveling spool 22 when observed in the short side direction. In the present embodiment, the loading / unloading priority spool 28 is arranged at a position equidistant from the first traveling spool 21 and the second traveling spool 22 when observed in the short side direction. However, the loading / unloading priority spool 28 is not limited to being arranged at such a position.

[0067] The communication passage 34 is as Figure 6 shown connected to the first traveling spool 21 and the second traveling spool 22 via branch passages 34a and 34b respectively. Moreover, the communication passage 34 can be connected to the first traveling spool 21 and the second traveling spool 22 without crossing the spools 23 to 29.

[0068] In addition, in the block body 11a, openings of passages 21a to 27a, 21b to 27b connected to the respective spools 21 to 27 are formed on another side surface (not shown). Moreover, the openings of the passages 21a to 27a, 21b to 27b are connected to the respective actuators 2 to 8.

[0069] In the multi-control valve 1 of the present embodiment, the spools 21 to 26 of the drive systems for driving the actuators 2 to 8 are arranged in a row, so that the passages 32 to 34 can be easily formed. Also, the spools 28 and 29 of the auxiliary systems other than the spools 21 to 26 of the drive systems are arranged in a row beside the row of the spools 21 to 26 of the drive systems, so that the multi-control valve 1 can be formed compactly. Therefore, the loadability for construction machinery and the like can be improved.

[0070] Also, in the multi-control valve 1 of the present embodiment, the spool 28 for loading and unloading priority can be moved to the unloading position A1 and the priority position A3 respectively. Also, the spool 28 for loading and unloading priority discharges the working fluid flowing in the loading and unloading side passage 32 at the unloading position A1. Also, the spool 28 for loading and unloading priority causes the working fluid to flow preferentially to the loading and unloading side passage 32 at the priority position A3. Therefore, the spool 28 for loading and unloading priority has an unloading function and a loading and unloading priority function. Therefore, the unloading spool can be omitted in the multi-control valve 1. Thereby, the number of components in the multi-control valve 1 can be reduced.

[0071] In addition, in the multi-control valve 1 of the present embodiment, the spool 28 for loading and unloading priority is arranged between the first traveling spool 21 and the second traveling spool 22 when viewed in the column direction. Therefore, the length difference of the passages from the spool 28 for loading and unloading priority to the respective traveling spools 21 and 22 can be reduced. That is, the difference in the passage pressure loss from the spool for loading and unloading priority to the respective traveling spools can be reduced. In the present embodiment, the spool 28 for loading and unloading priority is arranged equidistantly from the respective traveling spools 21 and 22, so that the passage pressure losses from the spool 28 for loading and unloading priority to the respective traveling spools 21 and 22 can be made substantially the same.

[0072] In addition, in the multi-control valve 1 of the present embodiment, the pump port 35 is connected to the loading and unloading side passage 32. Therefore, the length of the passage from the pump port 35 to the respective spools 23 to 27 of the loading and unloading system can be reduced. Thereby, the passage pressure loss from the pump port 35 to the respective spools 23 to 27 of the loading and unloading system can be suppressed.

[0073] In addition, in the multi-control valve 1 of the present embodiment, the traveling side passage 33 is connected to the loading and unloading side passage 32 via the spool 28 for loading and unloading priority. Therefore, the passage connecting the pump port 35 and the loading and unloading side passage 32 can be omitted. Thereby, the number of passages formed on the valve block 11 can be suppressed.

[0074] <Regarding Other Embodiments>

[0075] In the multi-control valve 1 of the present embodiment, each of the first spool group 12 and the second spool group 13 includes spools 21 to 29 as an example, and may also include spools and valve bodies other than these. Further, in each of the first spool group 12 and the second spool group 13, the arrangement order of the spools 21 to 29 and the pressure compensation valve body 30 is not limited to the foregoing order and may be any order. Further, in the multi-control valve 1 of the present embodiment, the column direction in which the first spool group 12 and the second spool group 13 are arranged is the short side direction, but it may also be the height direction. The solenoid valves 14a to 14r do not have to be arranged as described above, and may be respectively arranged on both sides in the short side direction of the first spool group 12 and the second spool group 13.

[0076] In the multi-control valve 1 of the present embodiment, the valve block 11 includes a block main body 11a, a first solenoid valve block 11b, and a second solenoid valve block 11c, but they may be integrally formed. In the valve block 11 of the present embodiment, the loading / unloading side passage 32, the traveling side passage 33, and the communication passage 34 are arranged in the short side direction between the first spool group 12 and the second spool group 13, but they do not have to be arranged in this way. For example, at least one of the traveling side passage 33, the communication passage 34, and the loading / unloading side passage 32 may be formed on the other side in the short side direction of the first spool group 12. Further, at least one of the traveling side passage 33, the communication passage 34, and the loading / unloading side passage 32 may not extend to one end or the other end in the long side direction.

[0077] <Exemplary Embodiment>

[0078] The multi-control valve in the first aspect includes: a first spool group, which includes: a bucket spool for controlling the flow of the working fluid supplied to the bucket cylinder, a boom spool for controlling the flow of the working fluid supplied to the boom cylinder, an arm spool for controlling the flow of the working fluid supplied to the arm cylinder, a first travel spool for controlling the flow of the working fluid supplied to the first travel motor, a second travel spool for controlling the flow of the working fluid supplied to the second travel motor, and a swing spool for controlling the flow of the working fluid supplied to the swing motor; a valve block, which is formed with a loading / unloading side passage connecting the bucket spool, the boom spool, the arm spool and the swing spool and a travel side passage connecting the first travel spool and the second travel spool, and is inserted through by each spool of the first spool group in parallel with each other; and a second spool group, which includes: a regeneration spool for controlling the flow of the working fluid supplied from the rod side port of the boom cylinder to the head side port; and a loading / unloading priority spool for making the working fluid preferentially flow to the loading / unloading side passage by controlling the flow rate of the working fluid flowing in the travel side passage, and each spool is inserted through the valve block in a form parallel to each spool of the first spool group; each spool of the first spool group is arranged in a row on the valve block in a specified direction, and each spool of the second spool group is arranged in a row on the valve block in a specified direction and forms a row different from each spool of the first spool group.

[0079] According to the above aspect, since the spools of the drive system that are actuators for each cylinder and each motor are arranged in a row, the formation of the passage can be facilitated. Also, by arranging the spools of the auxiliary system other than the spools of the drive system in a row beside the row of the spools of the drive system, the multi-control valve can be formed compactly. Therefore, the loadability on the machine can be improved.

[0080] In the multi-control valve in the second aspect, in the multi-control valve in the first aspect, the loading / unloading priority spool can be located at the unloading position and the priority position respectively. At the unloading position, the working fluid flowing in the loading / unloading side passage is discharged, and at the priority position, the working fluid preferentially flows to the loading / unloading side passage.

[0081] According to the above aspect, the loading / unloading priority spool can be moved to the unloading position and the priority position respectively. Also, the loading / unloading priority spool discharges the working fluid flowing in the loading / unloading side passage at the unloading position. Also, the loading / unloading priority spool makes the working fluid preferentially flow to the loading / unloading side passage at the priority position. Therefore, the loading / unloading priority spool has an unloading function and a loading / unloading priority function. Therefore, the unloading spool can be omitted in the multi-control valve. Therefore, the number of components in the multi-control valve can be reduced.

[0082] In the multi-control valve of the third aspect, in the multi-control valve of the first or second aspect, the first spool for travel and the second spool for travel are arranged separately from each other in a specified direction, and the spool for loading / unloading priority is arranged between the first spool for travel and the second spool for travel when viewed in the column direction in which the first spool group and the second spool group are arranged.

[0083] According to the above aspect, the spool for loading / unloading priority is arranged between the first spool for travel and the second spool for travel when viewed in the column direction. Therefore, the difference in the lengths of the passages from the spool for loading / unloading priority to the respective spools for travel can be reduced. That is, the difference in the passage pressure losses from the spool for loading / unloading priority to the respective spools for travel can be reduced.

[0084] In the multi-control valve of the fourth aspect, in the multi-control valve of any one of the first to third aspects, the valve block includes a pump port, and the pump port is connected to the passage on the loading / unloading side.

[0085] According to the above aspect, the pump port is connected to the passage on the loading / unloading side. Therefore, the length of the passage from the pump port to each spool in the loading / unloading system can be reduced. Thereby, the passage pressure loss from the pump port to each spool in the loading / unloading system can be suppressed.

[0086] In the multi-control valve of the fifth aspect, in the multi-control valve of any one of the first to fourth aspects, the passage on the travel side is connected to the passage on the loading / unloading side via the spool for loading / unloading priority.

[0087] According to the above aspect, the passage on the travel side is connected to the passage on the loading / unloading side via the spool for loading / unloading priority. Therefore, the passage connecting the pump port and the passage on the loading / unloading side can be omitted. Thereby, the number of passages formed in the valve block can be suppressed.

[0088] In the multi-control valve of the sixth aspect, in the multi-control valve of any one of the first to fifth aspects, the passage on the loading / unloading side and the passage on the travel side are formed between the first spool group and the second spool group in the column direction in which the first spool group and the second spool group of the valve block are arranged.

[0089] According to the above aspect, the passage on the loading / unloading side and the passage on the travel side are formed in the valve block and are formed between the first spool group and the second spool group in the column direction. Therefore, the passages connecting the passage on the loading / unloading side and the passage on the travel side to the respective spools of the first spool group and the second spool group can be formed to be short. Also, since the passage on the loading / unloading side and the passage on the travel side are formed between the first spool group and the second spool group in the column direction, the spaces on both sides in the column direction of the valve block can be effectively utilized.

[0090] In the multi-control valve according to the seventh aspect, in the multi-control valve according to the sixth aspect, a communication path that communicates the first travel motor and the second travel motor when supplying working fluid to the first travel motor and the second travel motor is formed on the valve block, and the communication path is formed between the first spool group and the second spool group on the valve block in the column direction in which the first spool group and the second spool group are arranged.

[0091] According to the above aspect, the communication path is formed between the first spool group and the second spool group on the valve block in the column direction in which the first spool group and the second spool group are arranged. Therefore, the communication path can be formed near the first travel spool and the second travel spool, so the length of the communication path can be shortened. Also, since the communication path is formed between the first spool group and the second spool group, the space on both sides in the column direction of the valve block can be effectively utilized. In addition, since the communication path does not cross the respective passages included in the first spool group and the second spool group, the influence of the change in the passage pressure loss during the operation of other spools can be suppressed.

Claims

1. A multi-control valve, characterized in that: have: a first valve core group, comprising: a bucket valve core for controlling the flow of working fluid supplied to a bucket cylinder, an arm valve core for controlling the flow of working fluid supplied to an arm cylinder, an arm valve core for controlling the flow of working fluid supplied to an arm cylinder, a first travel valve core for controlling the flow of working fluid supplied to a first travel motor, a second travel valve core for controlling the flow of working fluid supplied to a second travel motor, and a rotation valve core for controlling the flow of working fluid supplied to a rotation motor; a valve block having a loading and unloading passage connected to the bucket valve core, the arm valve core, the boom valve core, and the swing valve core, and a travel passage connected to the first travel valve core and the second travel valve core, and having valve cores of the first valve core group inserted therethrough in parallel; and A second valve core group, comprising: a regeneration valve core for controlling the flow of the working fluid supplied from the rod side port of the boom cylinder to the head side port; and a loading and unloading priority valve core for controlling the flow rate of the working fluid flowing in the travel side passage so that the working fluid preferentially flows to the loading and unloading side passage, and each valve core is inserted through the valve block in a form parallel to each valve core of the first valve core group; The valve cores of the first valve core group are arranged in a row along a specified direction on the valve block; The valve elements of the second valve element group are arranged in a row along a predetermined direction on the valve block, and form a row different from that of the valve elements of the first valve element group.

2. The multi-control valve according to claim 1, characterized in that: The loading and unloading priority valve core can be located at an unloading position and a priority position, respectively. The working fluid flowing in the loading and unloading side passage is discharged at the unloading position, and the working fluid is preferentially flowed to the loading and unloading side passage at the priority position.

3. The multi-control valve according to claim 1, characterized in that: The first travel valve core and the second travel valve core are arranged to be separated from each other in a predetermined direction; The loading and unloading priority valve element is disposed between the first traveling valve element and the second traveling valve element when viewed in a row direction in which the first valve element group and the second valve element group are arranged.

4. The multi-control valve according to claim 1, characterized in that: The valve block includes a pump port; The pump port is connected to the loading and unloading side passage.

5. The multi-control valve according to claim 1, characterized in that: The travel-side passage is connected to the loading / unloading-side passage via the loading / unloading priority valve body.

6. The multi-control valve according to claim 1, characterized in that: The loading and unloading side passage and the traveling side passage are formed between the first valve body group and the second valve body group in the row direction in which the first valve body group and the second valve body group of the valve block are arranged.

7. The multi-control valve according to claim 6, characterized in that: The valve block is formed with a communication passage for connecting the first travel motor and the second travel motor when the working fluid is supplied to the first travel motor and the second travel motor; The communication passage is formed on the valve block between the first valve core group and the second valve core group in a row direction in which the first valve core group and the second valve core group are arranged.

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