JP2013249897A - Multiple valve device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress oil leak or the like by reducing the number of connection ports in joining surfaces to a requisite minimum when pressure oil is supplied to a multiple valve device by two hydraulic pumps.SOLUTION: A valve housing 12 of a multiple valve device 11 is divided into two blocks in the vertical direction, a first housing block 13 and a second housing block 14. A total of four connection ports 67C, 69C, 73C, 74C are disposed at locations of joining surfaces 13B, 14A between the first housing block 13 and the second housing block 14. In supplying pressure oil to all control valves 26, 30, 34, 38, 47, 48, 54, 55, and 61 from a first and a second hydraulic pumps 77, 79, the number of the connection ports 67C, 69C, 73C, and 74C is reduced to a requisite minimum to suppress an oil leak or the like in between the joining surfaces 13B, 14A.

Description

  The present invention relates to a multiple valve device that is mounted on a construction machine such as a hydraulic excavator and is suitably used for driving and controlling a traveling hydraulic actuator and a working hydraulic actuator.

  In general, in a construction machine such as a hydraulic excavator, pressure oil is supplied to and discharged from a hydraulic actuator (for example, a hydraulic motor, a hydraulic cylinder, etc.) from a hydraulic source such as a hydraulic pump. A multi-valve device comprising a spool valve (direction control valve) is provided.

  This type of prior art multiple valve device has a plurality of spool sliding holes, a valve housing provided with a hydraulic source side oil passage and an actuator side oil passage respectively communicating with the spool sliding holes, A plurality of spools are provided which are inserted into the respective spool sliding holes of the valve housing and selectively connect and disconnect the hydraulic source side oil passage and the actuator side oil passage.

  Moreover, as a valve housing used for such a multiple valve device, for example, a stack type in which three or more housing blocks are abutted and overlapped with each other on a mating surface, and a two-divided 2 is formed. Three types are known: a two-part type in which two housing blocks are brought into contact with each other at the position of the mating surface, and a mono-block type in which the whole is formed as a single housing block (for example, Patent Document 1, 2, 3, 4).

Japanese Utility Model Publication No. 50-55921 JP 59-186502 A JP-A-4-73404 JP 2000-205426 A

  By the way, in the above-described prior art, for example, in the case of a stack type valve housing, since three or more housing blocks are abutted and overlapped with each other on the mating surfaces, the mating surfaces of the respective housing blocks are highly accurate. There is a problem that it is necessary to finish the work, and it takes time to finish the work for each block, resulting in poor workability during manufacture and assembly. In addition, since the monoblock type valve housing is a single large block body, there is a problem that it becomes a heavy object and the handling property and workability at the time of transfer and transportation deteriorate.

  On the other hand, the two-part valve housing according to the prior art can be about half the weight of one block as compared with the monoblock type, and the structure of the core that is a part of the mold can be simplified. it can. In addition, the number of mating surfaces can be reduced compared to the stack type, and there is an advantage that occurrence of defective seals can be reduced. However, in this case, it is necessary to increase the size of each housing block in order to increase the number of built-in spools. When the size of the housing block is increased and the area of the mating surface is increased, when high-pressure hydraulic fluid flows through the connection port of the oil passage on the mating surface, poor sealing or oil leakage occurs at the mating surface position. there is a possibility.

  In particular, when two hydraulic pumps are used as the hydraulic source, for example, the hydraulic oil from the two hydraulic pumps may be supplied to the boom cylinder and the arm cylinder of the excavator. However, when the number of such joining points is increased, the number of connection ports of the oil passage on the mating surface is increased, which increases the possibility of oil leakage on the mating surface.

  The present invention has been made in view of the above-described problems of the prior art, and the object of the present invention is to provide a mating surface even when pressure oil is supplied between two hydraulic pumps while taking advantage of the two-part valve housing. It is an object of the present invention to provide a multi-valve device that can reduce the number of connection ports of an oil passage to the minimum necessary and suppress the occurrence of oil leakage and the like.

  In order to solve the above-described problem, the present invention provides a valve housing provided with six or more spool sliding holes communicating with a plurality of hydraulic source side oil passages and a plurality of actuator side oil passages, And six or more spools that are inserted into the respective spool sliding holes and communicate with and shut off the hydraulic source side oil passage and the actuator side oil passage, and include first and second hydraulic pumps. However, the present invention is applied to a multiple valve device configured to control the flow of pressure oil by two hydraulic sources using the plurality of spools.

  A feature of the configuration adopted by the invention of claim 1 is that the valve housing has a one-side housing block having three or more spools which are abutted and separated from each other at the position of the facing mating surfaces, and the rest. The first hydraulic pump is configured to be divided into two or more other housing blocks including three or more spools, and the first hydraulic pump is provided in any one of the one side and other side housing blocks. Connected to a hydraulic pressure source side oil passage, the pressure oil from the first hydraulic pump is from a position upstream of the spool disposed near the mating surface in the one housing block. The second hydraulic pump is configured to be supplied to a part of the plurality of spools provided in the other housing block through the mating surface. Provided in connection with the oil pressure source side oil passage provided in the other housing block of the blocks, and the pressure oil from the second hydraulic pump is disposed at a position close to the mating surface in the other housing block. According to another aspect of the present invention, a part of the plurality of spools provided in the one housing block is supplied through the mating surface from a position upstream of the spool.

  The feature of the configuration adopted by the invention of claim 2 is that the valve housing has one side housing block having three or more spools which are abutted and separated from each other at the position of the facing mating surfaces, and the remaining three The first hydraulic pump is configured to be divided into two, that is, the other housing block having the spool described above, and the first hydraulic pump is provided with one of the one side and the other side housing blocks. Pressure oil from the first hydraulic pump is provided in connection with a side oil passage, and the mating is performed from a position upstream of the spool disposed at a position near the mating surface in the one housing block. The second hydraulic pump is connected to the one housing block through a surface and supplied to a part of the plurality of spools provided in the other housing block. A plurality of hydraulic source side oil passages connected to a hydraulic source side oil passage that is different from the hydraulic source side oil passage to which the first hydraulic pump is connected; and from the second hydraulic pump The pressure oil of one of the plurality of spools provided in the other housing block through the mating surface from a position upstream of the spool disposed at a position close to the mating surface in the one housing block. The configuration is such that the spool is supplied to a spool different from the part.

  According to a third aspect of the present invention, the one housing block is connected to the first one-side oil passage system and the second hydraulic pump, wherein the plurality of hydraulic source-side oil passages are connected to the first hydraulic pump. The second housing block is formed separately from the second one-side oil passage system to be connected, and the other housing block has the plurality of hydraulic source-side oil passages connected to the first hydraulic pump. An oil passage system and a second other-side oil passage system connected to the second hydraulic pump are separately formed, and the first one-side oil passage system formed in the one housing block includes: The second other oil passage system formed in the one housing block is configured to communicate with the first other oil passage system formed in the other housing block through the mating surface. Formed on the housing block It is configured to communicate through the mating surface to said second other-side oil passage lineages.

  The feature of the configuration adopted by the invention of claim 4 is that the valve housing has one side housing block having three or more spools which are abutted and separated from each other at the position of the facing mating surfaces, and the remaining three The first housing block is divided into two parts, the other housing block having the spool, and the one housing block is connected to the first hydraulic pump through the plurality of hydraulic source side oil passages. An oil passage system and a second one-side oil passage system connected to the second hydraulic pump are separately formed, and the other housing block includes the plurality of hydraulic source side oil passages in the first A first other-side oil passage system connected to the hydraulic pump and a second other-side oil passage system connected to the second hydraulic pump are separately formed and formed in the one-side housing block The first one-side oil passage system is The second one-side oil passage system formed in the one-side housing block is configured to communicate with the first other-side oil passage system formed in the other-side housing block through the mating surface. The present invention is configured to communicate with the second other oil passage system formed in the side housing block through the mating surface.

  According to a fifth aspect of the present invention, the first one-side oil passage system receives pressure oil from the first hydraulic pump from the spool disposed at a position close to the mating surface in the one-side housing block. The second other oil passage system is supplied from the second hydraulic pump through the mating surface to the first other oil passage system of the other housing block. The second one-side oil passage system of the one-side housing block through the mating surface from a position upstream of the spool disposed at a position close to the mating surface in the other-side housing block. It is configured to supply to.

  According to a sixth aspect of the present invention, the first one-side oil passage system receives pressure oil from the first hydraulic pump from the spool disposed at a position close to the mating surface in the one-side housing block. Is configured to supply the first other-side oil passage system of the other-side housing block from the upstream position through the mating surface, and the second one-side oil passage system is connected to the second hydraulic pump. The second other-side oil passage system of the other-side housing block through the mating surface from a position upstream of the spool disposed in the position near the mating surface in the one-side housing block. It is configured to supply to.

  According to the invention of claim 7, any one of the one side housing block and the other side housing block is formed by cutting out the four corners of the housing block, and is formed between the mating surfaces. Are provided with four recessed portions that become seat surfaces for fastening bolts, and the seat surface portions of the four recessed portions engage the one side housing block and the other side housing block using a plurality of bolts. High-pressure side passing through the position of the mating surface connected to the first hydraulic pump or the second hydraulic pump among the plurality of hydraulic source-side oil passages The oil passage is arranged at a position closer to the center side of the mating surface.

  According to an eighth aspect of the present invention, two spools of the plurality of spools in which the supplied pressure oils merge with each other are provided in the same housing block on one side of the one side and other side housing blocks. It is configured.

  According to a ninth aspect of the present invention, the valve housing constitutes a plurality of directional control valves used for a construction machine together with the spools that are respectively inserted and fitted into the spool sliding holes, Two spools in which the supplied pressure oils merge with each other are a first boom spool and a second boom spool provided for controlling the boom cylinder of the construction machine, or an arm cylinder. The first arm spool and the second arm spool are provided to control the movement.

  As described above, according to the first aspect of the present invention, the predetermined spool among the plurality of spools provided in one of the one side housing block and the other side housing block includes the first spool. The pressure oil from the hydraulic pump can be supplied through the oil pressure source side oil passage, and the pressure oil from the first hydraulic pump is also joined to a part of the plurality of spools provided in the other housing block. For this purpose, it is only necessary to provide one connection port at the position of the mating surface. In addition, pressure oil from the second hydraulic pump can be supplied to a predetermined spool among the plurality of spools provided in the other housing block through the hydraulic power source side oil passage, and one housing block Pressure oil from the second hydraulic pump can also be supplied through a mating surface to some of the plurality of spools provided therein, and for this purpose, another connection port is provided at the position of the mating surface. Just install one. As a result, the number of connection ports of the oil passage on the mating surface can be reduced to the minimum necessary even when pressure oil is supplied between the two hydraulic pumps while utilizing the advantages of the two-part valve housing. Etc. can be suppressed.

  Further, the valve housing of the multiple valve device can be constituted by one side and other side housing blocks formed by dividing the valve housing into two parts (that is, one and the other housing block), and these two housing blocks are aligned to face each other. They can abut or separate from each other at the surface position. Within the one-side housing block, three or more spool sliding holes can be arranged with a three-dimensional structure in a direction parallel to and perpendicular to the mating surface. Even in the block, the remaining three to six spool sliding holes can be arranged with another three-dimensional structure in a direction parallel to and perpendicular to the mating surface. For this reason, when increasing the number of spool sliding holes (spool valves), the housing block can be sized in the direction perpendicular to the mating surface, and there is no need to increase the dimension in the direction parallel to the mating surface. The area of the mating surface can be made as small as possible.

  According to the second aspect of the present invention, pressure oil from the first hydraulic pump is hydraulically applied to a predetermined spool among a plurality of spools provided in either one of the one side housing block and the other side housing block. The pressure oil from the first hydraulic pump can be supplied through the mating surface to a part of the plurality of spools provided in the other housing block, and can be supplied through the source side oil passage. It is only necessary to provide one connection port at the position of the mating surface. Also, a hydraulic pressure source to which the first hydraulic pump is connected among a plurality of hydraulic source side oil passages provided in one housing block is connected to a spool different from the spool provided in one housing block. Pressure oil from the second hydraulic pump can be supplied by a hydraulic source side oil passage different from the side oil passage, and also in a spool different from some of the plurality of spools provided in the other housing block, The pressure oil from the second hydraulic pump can be supplied through the mating surface. To this end, it is only necessary to provide one other connection port at the position of the mating surface. As a result, the number of connection ports of the oil passage on the mating surface can be reduced to the minimum necessary even when pressure oil is supplied between the two hydraulic pumps while utilizing the advantages of the two-part valve housing. Etc. can be suppressed.

  According to the invention of claim 3, the first one-side oil passage system formed in one housing block communicates with the first other-side oil passage system formed in the other housing block through a mating surface. The second one-side oil passage system formed in the one housing block can be communicated with the second other-side oil passage system formed in the other housing block through the mating surface.

  The inventions of claims 4 to 6 can provide substantially the same effects as those of the inventions of claims 1 to 3 described above. In the invention of claim 5, the pressure oil from the first hydraulic pump can be supplied to the spool in the one-side housing block via the first one-side oil passage system, and the pressure oil from the first hydraulic pump can be supplied. The first other oil passage system of the other housing block can be supplied through the mating surface. The pressure oil from the second hydraulic pump can be supplied to the spool in the other side housing block via the second other side oil passage system, and also to the second one side oil passage system of the one side housing block. Can be supplied through mating surfaces. On the other hand, in the invention of claim 6, the pressure oil from the second hydraulic pump can be supplied to the spool in the one side housing block via the second one side oil passage system, and the pressure from the second hydraulic pump can be supplied. Oil can be supplied to the second other oil passage system of the other housing block through the mating surface.

  According to the seventh aspect of the present invention, the one side housing block and the other side housing block can be fastened by using a plurality of bolts in a state where the one side housing block and the other side housing block are brought into contact with each other at the mating surface position. The oil passage can be disposed at a position closer to the center side of the mating surface. Accordingly, the oil passage on the high pressure side passing through the position of the mating surface can be provided at a position closer to the center side of the mating surface than the oil passage on the low pressure side, and the pressure oil flowing through these oil passages Leakage from the position to the outside can be suppressed.

  According to the eighth aspect of the present invention, the pressure oil discharged from the first and second hydraulic pumps can be merged in the same housing block and supplied to the two spools. It is not necessary to provide at the position of the mating surface of the block. As a result, the number of connection ports on the mating surfaces can be reduced, and the occurrence of oil leakage or the like can be suppressed.

  According to the ninth aspect of the present invention, as a plurality of directional control valves that individually drive and control the traveling hydraulic actuator and the working hydraulic actuator by mounting a multiple valve device on a construction machine such as a hydraulic excavator, for example. Multiple valve devices can be used. Among these, the first boom spool and the second boom spool provided for controlling the boom cylinder are provided in the same housing block, so that the pressure oil discharged from the first and second hydraulic pumps is provided. Can be combined in one housing block and supplied to two spools. Also, the first arm spool and the second arm spool provided for controlling the arm cylinder are also provided in the same housing block, so that the pressures discharged from the first and second hydraulic pumps. Oil can be merged in one housing block and fed to two spools.

1 is an overall view showing a hydraulic excavator equipped with a multiple valve device according to a first embodiment of the present invention. It is a perspective view which expands and shows the multiple valve apparatus in FIG. It is the perspective view which looked at the multiple valve apparatus from the opposite side to FIG. It is the longitudinal cross-sectional view which looked at the multiple valve apparatus from the arrow IV-IV direction in FIG. It is the longitudinal cross-sectional view which looked at the multiple valve apparatus from the arrow VV direction in FIG. It is the longitudinal cross-sectional view which looked at the multiple valve apparatus from the arrow VI-VI direction in FIG. FIG. 7 is a cross-sectional view of the one-side housing block as viewed from the direction of arrows VII-VII in FIG. 5 together with the left and right traveling control valves and the like. It is the cross-sectional view which looked at the 1 side housing block from the arrow VIII-VIII direction in FIG. 5 with the control valve for buckets, a backup control valve, etc. It is the cross-sectional view which looked at the 1 side housing block from the arrow IX-IX direction in FIG. 5 with the relief valve. It is the cross-sectional view which looked at the other side housing block from the arrow XX direction in FIG. 5 with the boom control valve. It is the cross-sectional view which looked at the other side housing block from the arrow XI-XI direction in FIG. 5 with the control valve for arms. It is the cross-sectional view which looked at the other side housing block from the arrow XII-XII direction in FIG. It is the cross-sectional view which looked at the other side housing block from the arrow XIII-XIII direction in FIG. FIG. 2 is a hydraulic circuit diagram of a multiple valve device used in the hydraulic excavator shown in FIG. 1. It is a hydraulic circuit diagram of the multiple valve apparatus by a comparative example. It is a hydraulic-circuit figure of the multiple valve apparatus by 2nd Embodiment.

  Hereinafter, a case where the multiple valve device according to the embodiment of the present invention is mounted on a hydraulic excavator as a construction machine will be described as an example and described in detail with reference to the accompanying drawings.

  In the description of the embodiment, as a representative example of the multiple valve device, a total of four spool sliding holes are provided in one housing block, and a total of five spool sliding holes are provided in the other housing block. The case of providing is given as an example. However, the multiple valve device according to the present invention is not limited to this, and among the valve housings provided with 6 to 12 spool sliding holes, 3 to 6 spool slides are provided on one housing block. A moving hole may be provided, and 3 to 6 spool sliding holes may be provided in the other housing block.

  Here, FIG. 1 thru | or FIG. 14 has shown the multiple valve apparatus which concerns on the 1st Embodiment of this invention. In the figure, reference numeral 1 denotes a hydraulic excavator as a construction machine. The hydraulic excavator 1 is mounted on a crawler type lower traveling body 2 capable of self-propelling as shown in FIG. The upper revolving body 3 and a work device 7 to be described later are roughly configured. In this case, the upper swing body 3 of the hydraulic excavator 1 constitutes the vehicle body of the construction machine together with the lower traveling body 2. The upper turning body 3 has a turning frame 3A that is driven to turn on the lower traveling body 2, and a cab 4, a counterweight 5, a building cover 6, and the like, which will be described later, are provided on the turning frame 3A.

  Reference numeral 4 denotes a cab disposed on the left side of the front portion of the swivel frame 3A. The cab 4 is formed as a substantially rectangular box and defines a cab inside thereof. In addition to the driver's seat on which the operator is seated, an operation lever for operation, a travel lever (none of which are shown) and the like are provided inside the cab 4.

  Reference numeral 5 denotes a counterweight provided on the rear end side of the swing frame 3A. The counterweight 5 is detachably mounted on the rear end side of the swing frame 3A, and the entire upper swing body 3 with respect to the work device 7 on the front side. The weight balance is taken. A building cover 6 (described later) that houses an engine (not shown) or the like is provided on the front side of the counterweight 5.

  A building cover 6 is located between the cab 4 and the counterweight 5 and is erected on the turning frame 3A. The building cover 6 is formed using, for example, a plurality of metal panels made of thin steel plates, and defines a machine room (not shown) that houses an engine or the like inside. In the building cover 6, hydraulic pumps 77 and 79 (see FIG. 14) described later that are driven to rotate by the engine are provided. In the building cover 6, a multiple valve device 11 described later is provided at a position close to the cab 4.

  Reference numeral 7 denotes a working device provided at the front of the upper swing body 3 so as to be able to move up and down. The working device 7 includes a boom 8 whose base end is attached to the turning frame 3A so as to be able to move up and down, and a tip of the boom 8 The arm 9 is mounted on the side so as to be able to move up and down, and for example, a bucket 10 as a work tool that is rotatably provided on the distal end side of the arm 9 for excavation work such as earth and sand.

  The boom 8 of the working device 7 is moved up and down with respect to the revolving frame 3A by the boom cylinder 8A, and the arm 9 is moved up and down by the arm cylinder 9A on the tip side of the boom 8. The bucket 10 as a work tool is rotated up and down by a bucket cylinder 10A as a work tool cylinder on the tip side of the arm 9.

  Next, reference numeral 11 denotes a multiple valve device employed in the first embodiment. This multiple valve device 11 includes a valve housing 12 and spools 27, 31, 35, which will be described later, as shown in FIGS. , 39, 49, 51, 56, 58, 62, a relief valve 88, and the like. And the valve housing 12 of the multiple valve apparatus 11 is divided into two by a one-side housing block 13 and an other-side housing block 14 which will be described later, as shown in FIGS.

  Here, the one-side housing block 13 and the other-side housing block 14 are arranged in a left and right direction (X-axis direction in FIG. 2) and a front and rear direction (Y-axis direction) parallel to mating surfaces 13B and 14A described later. ) And a block having a rectangular parallelepiped shape extending in the upper and lower directions (Z-axis direction) perpendicular to the mating surfaces 13B and 14A. The one-side housing block 13 and the other-side housing block 14 are abutted so as to be separable from each other at the positions of the mating surfaces 13B and 14A.

  Reference numeral 13 denotes a one-side housing block which is a half of the valve housing 12, and the one-side housing block 13 is molded as a rectangular parallelepiped cast product as shown in FIGS. Yes. The one-side housing block 13 has a total of six surfaces including an upper surface 13A (hereinafter referred to as an upper surface 13A), a lower mating surface 13B, front and rear side surfaces 13C and 13D, and left and right side surfaces 13E and 13F. have.

  As shown in FIG. 2, the one-side housing block 13 is provided with a later-described pump port 65 opened at a position above the later-described cover 81 </ b> A on the front side surface 13 </ b> C. Further, on the front side surface 13C, pressure oil supply / discharge ports 29A, 29B and pressure oil supply / discharge ports 37A, 37B, which will be described later, are opened at positions separated from each other in the left and right directions (X-axis direction). ing. As shown in FIG. 3, the rear side surface 13D is opened at positions spaced leftward and rightward (in the X-axis direction), and pressure oil supply / discharge ports 33A and 33B and pressure oil supply / discharge ports described later are opened. 41A and 41B are provided.

  Reference numeral 14 denotes an other housing block constituting another half of the valve housing 12, and the other housing block 14 is also formed as a rectangular parallelepiped block (casting) by means such as casting. The other housing block 14 has a total of six parts including an upper mating surface 14A, a lower other surface 14B (hereinafter referred to as a lower surface 14B), front and rear side surfaces 14C and 14D, and left and right side surfaces 14E and 14F. Has a surface.

  As shown in FIG. 2, the other side housing block 14 is provided with a later-described pump port 71 opened at a position lower than a later-described cover 85 </ b> A on the front side surface 14 </ b> C. A tank port 75 (described later) is provided open at a position on the left side in the X-axis direction. In addition, pressure oil supply / discharge ports 53A and 53B, which will be described later, are provided on the front side surface 14C so as to be spaced apart in the left and right directions (X-axis direction). As shown in FIG. 3, pressure oil supply / discharge ports 60A and 60B, which will be described later, and pressure oil supply / discharge ports 64A and 64B are separated from each other in the left and right directions (X-axis direction) on the rear side surface 14D. Is provided.

  Reference numeral 15 denotes a plurality of (for example, a total of four) recessed portions formed in the one-side housing block 13, and these recessed portions 15 are located at the four corners of the one-side housing block 13 at positions above the mating surface 13B. Are formed by notching each of the corners (that is, the corners between the front and rear side surfaces 13C and 13D and the left and right side surfaces 13E and 13F) into a L-shaped cross section. Has been.

  The lower surface side of each recessed portion 15 is a seat surface portion 15A for fastening bolts between the mating surface 13B, and these seat surface portions 15A are used to mount the one-side housing block 13 using a plurality of bolts 16, 16,. A fastening portion is configured to be fixed (coupled) to the other housing block 14 in an abutting state. And the recessed part 15 forms the volt | bolt mounting space for the volt | bolts 16 in the upper position of 15 A of seat surface parts.

  Here, the seat surface portion 15A (fastening portion) of each recessed portion 15 is provided at a position closer to the mating surface 13B than each spool valve including the bucket control valve 34 and the spare control valve 38, and the spool valve It arrange | positions in the position which becomes between the mating surfaces 13B. In addition, it is not always necessary to fasten one bolt 16 to the seating surface portion 15A of each recessed portion 15, and in some cases, two or more bolts 16 are fastened to one seating surface portion 15A. Also good.

  The other side housing block 14 is formed with screw holes 17 (see FIGS. 10 and 13) at positions facing the respective seating surface portions 15A above and below the mating surface 14A. The bolts 16 are respectively screwed. As a result, the one-side housing block 13 and the other-side housing block 14 are fixed in an abutting state by using a total of four bolts 16 and constitute the valve housing 12 of the multiple valve device 11.

  18, 19, 20, 21 are four spool sliding holes provided in the one-side housing block 13, and the spool sliding holes 18 to 21 are three-dimensional like the cover body 22 described later shown in FIG. 2. A structure is arranged in the one-side housing block 13. The spool sliding holes 18 to 21 extend in parallel to each other along the X-axis direction as shown in FIGS. 4, 5, 7, and 8, and are separated from each other in the Y-axis direction and the Z-axis direction. .

  Here, the number of spool sliding holes provided in the one-side housing block 13 is not limited to four, and a configuration may be adopted in which three spool sliding holes are provided as a minimum so as to form a three-dimensional structure. In this case, the one-side housing block 13 is provided with a total of three spool sliding holes 18, 19, and 20, for example, travel control valves 26 and 30 and a bucket control valve 34, which will be described later, for the spare control valve 38. The spool sliding hole 21 may be omitted.

  Of the spool sliding holes 18 to 21, the spool sliding holes 18 and 19 extend in parallel in the X-axis direction as shown in FIG. 7, and are arranged at a predetermined interval in the Y-axis direction. Further, as shown in FIG. 8, the spool sliding holes 20 and 21 also extend in parallel in the X-axis direction, and are arranged at a predetermined interval in the Y-axis direction. As shown in FIG. 4, the spool sliding holes 18 and 20 extend in parallel with each other along the X-axis direction, and are arranged at a predetermined interval in the Z-axis direction. Further, the spool sliding holes 19 and 21 also extend in parallel with each other along the X-axis direction as shown in FIG. 5, and are arranged at a predetermined interval in the Z-axis direction.

  Here, in the one-side housing block 13, annular oil grooves 18A and 18B are formed on the peripheral wall side of the spool sliding hole 18 so as to be spaced apart in the axial direction as shown in FIG. 7, and between the oil grooves 18A and 18B. Are formed with other annular oil grooves 18C, 18C. Further, another oil groove 18D, 18D is formed on the peripheral wall side of the spool sliding hole 18 at a position that is on the outer side in the axial direction than the oil grooves 18A, 18B.

  Of these oil grooves 18A to 18D, oil grooves 18A and 18B serve as oil grooves on the pressure oil supply / discharge side, communicate with pressure oil supply / discharge ports 29A and 29B for the running right, which will be described later, and the actuator-side oil passages. It constitutes. Each oil groove 18C serves as a high pressure side oil groove and communicates with a pump passage 66 on the pump port 65 side, which will be described later, and high pressure passages 68, 69, and each oil groove 18D serves as a low pressure side oil groove, which will be described later. It communicates with the side passage portion 70B of the low pressure passage 70 on the tank 78 side. These oil grooves 18C and 18D constitute a hydraulic pressure source side oil passage.

  Further, as shown in FIG. 7, the one-side housing block 13 has oil pressure grooves 19A and 19B on the pressure oil supply / discharge side constituting the actuator side oil passage and oil pressure grooves on the high pressure side on the peripheral wall side of the spool sliding hole 19. 19C and 19C and low-pressure side oil grooves 19D and 19D are formed to be separated from each other in the axial direction. These oil grooves 19C and 19D constitute a hydraulic pressure source side oil passage.

  On the peripheral wall side of the spool sliding hole 20, as shown in FIG. 8, the oil grooves 20A and 20B on the pressure oil supply / discharge side constituting the actuator side oil passage and the oil groove 20C on the high pressure side constituting the hydraulic source side oil passage are formed. , 20C and low-pressure side oil grooves 20D, 20D are formed to be separated from each other in the axial direction. Further, on the peripheral wall side of the spool sliding hole 21, as shown in FIG. 8, the oil grooves 21A and 21B on the pressure oil supply / discharge side constituting the actuator side oil passage and the oil on the high pressure side constituting the hydraulic source side oil passage are formed. The grooves 21C and 21C and the low-pressure side oil grooves 21D and 21D are formed to be separated from each other in the axial direction.

  22 is a cover body provided on the side surface 13F of the one-side housing block 13, and the cover body 22 has a total of four cylindrical protrusions 22A, 22B, 22C, 22D as shown in FIG. The cylindrical projecting portions 22A to 22D constitute hydraulic pilot portions 26B, 30B, 34B, and 38B of control valves 26, 30, 34, and 38, which will be described later.

  The cylindrical projecting portions 22A, 22B, 22C, and 22D are coaxial with the spool sliding holes 18, 19, 20, and 21, as shown in FIGS. Projecting from 13F in the X-axis direction. That is, the cylindrical projecting portions 22A to 22D extend in parallel with each other along the X-axis direction, like the spool sliding holes 18 to 21, and are arranged in a three-dimensional arrangement that is separated from each other in the Y-axis direction and the Z-axis direction. It is installed.

  Reference numeral 23 denotes another cover body provided on the side surface 13E of the one-side housing block 13, and the cover body 23 has a total of four short cylindrical portions 23A, 23B, 23C, and 23D as shown in FIG. The cylindrical portions 23A to 23D constitute hydraulic pilot portions 26A, 30A, 34A, and 38A of control valves 26, 30, 34, and 38, which will be described later.

  A cover body 24 is provided on the side surface 14F of the other housing block 14, and the cover body 24 has a total of five cylindrical projecting portions 24A, 24B, 24C, 24D, and 24E as shown in FIG. These cylindrical projecting portions 24A to 24E constitute hydraulic pilot portions 47B, 48B, 54B, 55B and 61B of control valves 47, 48, 54, 55 and 61, which will be described later.

  Cylindrical protrusions 24A, 24B, 24C, 24D, and 24E are coaxial with housings 42, 43, 44, 45, and 46, which will be described later, as shown in FIGS. Projecting from the side surface 14F of the block 14 in the X-axis direction. That is, the cylindrical protrusions 24A to 24E extend in parallel with each other along the X-axis direction like the spool sliding holes 42 to 46, and are arranged in a three-dimensional arrangement relationship that is separated from each other in the Y-axis direction and the Z-axis direction. It is installed.

  Reference numeral 25 denotes another cover body provided on the side surface 14E of the other housing block 14, and the cover body 25 includes a total of five short cylindrical portions 25A, 25B, 25C, 25D, and 25E as shown in FIG. These cylindrical portions 25A to 25E constitute hydraulic pilot portions 47A, 48A, 54A, 55A, 61A of control valves 47, 48, 54, 55, 61, which will be described later.

  Reference numeral 26 denotes a traveling right direction control valve (hereinafter referred to as a traveling control valve 26) provided in the one-side housing block 13, and the traveling control valve 26 is disposed in the spool sliding hole 18 as shown in FIG. It is constituted by a spool valve formed by inserting the spool 27 into the shaft. The traveling control valve 26 has left and right hydraulic pilot portions 26A and 26B in the cover bodies 22 and 23 located on both sides in the axial direction of the spool 27, and the right hydraulic pilot portion 26B has a spool 27 therein. A spring 28 that is always biased toward the neutral position is provided.

  Here, the traveling control valve 26 displaces the spool 27 in the axial direction of the spool sliding hole 18 according to the pilot pressure supplied to the hydraulic pilot portions 26A and 26B from an operation valve (not shown) such as a traveling lever. The oil grooves 18A and 18B on the actuator side are selectively communicated and blocked with respect to the oil grooves 18C and 18D on the hydraulic power source side. Thus, the traveling control valve 26 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  29A and 29B are pressure oil supply / discharge ports provided on the side surface 13C of the one-side housing block 13, and the pressure oil supply / discharge ports 29A and 29B are respectively provided in the oil grooves 18A and 18B on the actuator side as shown in FIG. On the other hand, it opens on the side surface 13C of the one-side housing block 13 as shown in FIG. As shown in FIG. 14, the pressure oil supply / discharge ports 29A and 29B are provided with left and right traveling motors 2L and 2R that provide pressure oil discharged from a hydraulic pump 77 described later to the lower traveling body 2 (see FIG. 1). Among these, for example, it is supplied to and discharged from the right traveling motor 2R.

  Reference numeral 30 denotes a traveling left direction control valve (hereinafter referred to as a traveling control valve 30) provided in the one-side housing block 13. The traveling control valve 30 is spooled in the spool sliding hole 19 as shown in FIG. The spool valve is formed by inserting 31. The traveling control valve 30 has left and right hydraulic pilot portions 30A and 30B in the cover bodies 22 and 23 located on both sides in the axial direction of the spool 31, and the spool 31 is always neutral in the hydraulic pilot portion 30B. A spring 32 that biases toward the position is disposed.

  The traveling control valve 30 displaces the spool 31 in the axial direction of the spool sliding hole 19 in accordance with the pilot pressure supplied to the hydraulic pilot portions 30A and 30B from an operation valve (not shown) such as a traveling lever, and the actuator side The oil grooves 19A and 19B are selectively communicated and blocked with respect to the oil grooves 19C and 19D on the hydraulic power source side. Thus, the traveling control valve 30 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  33A and 33B are other pressure oil supply / discharge ports provided on the side surface 13D of the one-side housing block 13, and the pressure oil supply / discharge ports 33A and 33B are oil grooves 19A and 19B on the actuator side as shown in FIG. One side communicates with the other side, and the other side opens on the side surface 13D of the one side housing block 13 as shown in FIG. As shown in FIG. 14, the pressure oil supply / discharge ports 33A and 33B are, for example, the left of the left and right traveling motors 2L and 2R that provide the lower traveling body 2 with the pressure oil discharged from a hydraulic pump 79 described later. Is supplied to and discharged from the traveling motor 2L.

  Reference numeral 34 denotes a directional control valve for work implement (hereinafter referred to as a bucket control valve 34) provided in the one-side housing block 13, and the bucket control valve 34 is disposed in the spool sliding hole 20 as shown in FIG. A spool valve is formed by inserting the spool 35. The bucket control valve 34 is provided with left and right hydraulic pilot portions 34A and 34B in the cover bodies 22 and 23 located on both axial sides of the spool 35, and the right hydraulic pilot portion 34B includes a spool 35. A spring 36 is disposed to constantly bias the spring toward the neutral position.

  The bucket control valve 34 displaces the spool 35 in the axial direction of the spool sliding hole 20 in accordance with the pilot pressure supplied to the hydraulic pilot portions 34A and 34B from an operation valve (not shown) such as a bucket operation lever. The oil grooves 20A and 20B on the side are selectively communicated and blocked with respect to the oil grooves 20C and 20D on the hydraulic power source side. Thereby, the bucket control valve 34 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  37A and 37B are pressure oil supply / discharge ports provided on the side surface 13C of the one-side housing block 13, and the pressure oil supply / discharge ports 37A and 37B are respectively provided in the oil grooves 20A and 20B on the actuator side as shown in FIG. On the other hand, it opens on the side surface 13C of the one-side housing block 13 as shown in FIG. The pressure oil supply / discharge ports 37 </ b> A and 37 </ b> B supply and discharge pressure oil to and from the bucket cylinder 10 </ b> A (see FIG. 1) of the work device 7.

  Reference numeral 38 denotes a spare directional control valve (hereinafter referred to as a spare control valve 38) provided in the one-side housing block 13. The spare control valve 38 is spooled in the spool sliding hole 21 as shown in FIG. The spool valve is formed by inserting 39. The spare control valve 38 is provided with left and right hydraulic pilot portions 38A and 38B in the cover bodies 22 and 23 located on both axial sides of the spool 39, and the right hydraulic pilot portion 38B includes a spool 39. A spring 40 is disposed to constantly urge the spring toward the neutral position.

  The spare control valve 38 displaces the spool 39 in the axial direction of the spool sliding hole 21 in accordance with the pilot pressure supplied from the operation valve (not shown) such as an operation lever to the hydraulic pilot portions 38A and 38B, The oil grooves 21A and 21B are selectively communicated and blocked with respect to the oil grooves 21C and 21D on the hydraulic power source side. Thereby, the spare control valve 38 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  41A and 41B are other pressure oil supply / discharge ports provided on the side surface 13D of the one-side housing block 13, and these pressure oil supply / discharge ports 41A and 41B are oil grooves 21A and 21B on the actuator side as shown in FIG. One side communicates with the other side, and the other side opens on the side surface 13D of the one side housing block 13 as shown in FIG. The pressure oil supply / discharge ports 41A and 41B supply / discharge pressure oil to / from a spare hydraulic actuator (not shown).

  Reference numerals 42, 43, 44, 45, 46 denote five spool sliding holes provided in the other housing block 14, and the spool sliding holes 42 to 46 correspond to the three-dimensional structure corresponding to the cover body 24 shown in FIG. And arranged in the other housing block 14. The spool sliding holes 42 to 46 extend in parallel to each other along the X-axis direction as shown in FIGS. 4, 5, and 10 to 12, and are separated from each other in the Y-axis direction and the Z-axis direction. .

  Here, the number of spool sliding holes provided in the other housing block 14 is not limited to five, and a configuration may be adopted in which three spool sliding holes are provided as a minimum so as to form a three-dimensional structure. In this case, the other housing block 14 is provided with a total of three spool sliding holes 42, 44, 46, for example, a boom control valve 47, an arm control valve 54, and a turning control valve 61. 48, the spool sliding holes 43 and 45 of the arm control valve 55 may be omitted.

  Of the spool sliding holes 42 to 46, the spool sliding holes 42 and 43 extend in parallel in the X-axis direction and are arranged at a predetermined interval in the Y-axis direction as shown in FIG. Further, as shown in FIG. 11, the spool sliding holes 45 and 46 extend in parallel in the X-axis direction and are arranged at a predetermined interval in the Y-axis direction. Further, as shown in FIG. 4, the spool sliding holes 42 and 44 extend in parallel with each other along the X-axis direction, and are arranged at intervals in the Z-axis direction. On the other hand, as shown in FIG. 5, the spool sliding holes 45 are spaced apart in the Z-axis direction between the spool sliding holes 43 and 46, and these spool sliding holes 43, 45, and 46 They extend parallel to each other along the axial direction.

  Here, in the other housing block 14, annular oil grooves 42A and 42B are formed on the peripheral wall side of the spool sliding hole 42 so as to be spaced apart in the axial direction, as shown in FIG. 10, and between the oil grooves 42A and 42B. Are formed with other annular oil grooves 42C, 42C. Further, on the peripheral wall side of the spool sliding hole 42, other oil grooves 42D and 42D are formed at positions outside the oil grooves 42A and 42B in the axial direction.

  Of these oil grooves 42A to 42D, the oil grooves 42A and 42B become oil grooves on the pressure oil supply / discharge side, communicate with boom pressure oil supply / discharge ports 53A and 53B, which will be described later, and constitute an actuator side oil passage. To do. Each oil groove 42C serves as a high-pressure side oil groove and communicates with a high-pressure passage 69 on the hydraulic pump 77, which will be described later, and each oil groove 42D serves as a low-pressure side oil groove, which will be described later. It communicates with the direction passage portion 76B. The oil groove 42C constitutes a hydraulic source side oil passage.

  Further, as shown in FIG. 10, the other side housing block 14 is provided with pressure oil supply / discharge side oil grooves 43A and 43B constituting an actuator side oil passage and a high pressure side oil groove on the peripheral wall side of the spool sliding hole 43. 43C, 43C and low pressure side oil grooves 43D, 43D are formed to be spaced apart from each other in the axial direction. The oil groove 43C constitutes a hydraulic source side oil passage.

  On the peripheral wall side of the spool sliding hole 44, as shown in FIG. 11, the pressure oil supply / discharge side oil grooves 44A and 44B constituting the actuator side oil passage and the high pressure side oil groove 44C constituting the hydraulic source side oil passage are formed. 44C and oil grooves 44D, 44D on the low pressure side are formed so as to be separated from each other in the axial direction. Further, on the peripheral wall side of the spool sliding hole 45, as shown in FIG. 11, oil grooves 45A and 45B on the pressure oil supply / discharge side constituting the actuator side oil passage and oil on the high pressure side constituting the hydraulic source side oil passage are formed. The grooves 45C and 45C and the low-pressure side oil grooves 45D and 45D are formed to be separated from each other in the axial direction.

  Further, as shown in FIG. 12, on the peripheral wall side of the spool sliding hole 46, oil grooves 46A and 46B on the pressure oil supply / discharge side constituting the oil passage on the actuator side, oil grooves 46C and 46C on the high pressure side, The oil grooves 46D, 46D on the side are formed so as to be separated from each other in the axial direction. These oil grooves 46C and 46D constitute a hydraulic pressure source side oil passage.

  Reference numerals 47 and 48 denote boom direction control valves (hereinafter referred to as boom control valves 47 and 48) provided in the other housing block 14. Among the boom control valves 47 and 48, one boom control valve 47 is provided. As shown in FIG. 10, it is constituted by a spool valve in which a first boom spool 49 is inserted into the spool sliding hole 42. The boom control valve 47 is located on both axial sides of the boom spool 49 and has left and right hydraulic pilot portions 47A and 47B in the cover bodies 24 and 25, and the right hydraulic pilot portion 47B includes a boom. A spring 50 that urges the spool 49 toward the neutral position is provided.

  Here, the boom control valve 47 moves the boom spool 49 in the axial direction of the spool sliding hole 42 according to the pilot pressure supplied to the hydraulic pilot portions 47A and 47B from an operation valve (not shown) such as a boom operation lever. The oil grooves 42A and 42B on the actuator side are selectively communicated and blocked with respect to the oil grooves 42C and 42D on the hydraulic power source side. Thereby, the boom control valve 47 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  The other boom control valve 48 among the boom control valves 47 and 48 is constituted by a spool valve formed by inserting a second boom spool 51 into the spool sliding hole 43. The other boom control valve 48 is located on both axial sides of the boom spool 51 and has left and right hydraulic pilot portions 48A and 48B in the cover bodies 24 and 25. The right hydraulic pilot portion 48B includes A spring 52 that urges the boom spool 51 toward the neutral position at all times is provided.

  Here, as with the boom control valve 47 described above, the boom control valve 48 moves the boom spool 51 in the axial direction of the spool sliding hole 43 according to the pilot pressure supplied from the operation valve to the hydraulic pilot portions 48A and 48B. The oil grooves 43A and 43B on the actuator side are selectively communicated and blocked with respect to the oil grooves 43C and 43D on the hydraulic power source side. Thereby, the boom control valve 48 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  53A and 53B are pressure oil supply / discharge ports provided on the side surface 14C of the housing block 14. The pressure oil supply / discharge ports 53A and 53B are connected to the oil grooves 42A and 42B on the actuator side as shown in FIG. It communicates with oil grooves 43A and 43B via merging passages 93A and 93B, which will be described later, and opens on the side surface 14C of the housing block 14 on the other side as shown in FIG. The pressure oil supply / discharge ports 53 </ b> A and 53 </ b> B supply and discharge pressure oil to and from the boom cylinder 8 </ b> A (see FIG. 1) of the work device 7.

  That is, the boom control valves 47 and 48 join together the pressure oil discharged from the hydraulic pumps 77 and 79, which will be described later, in the other side housing block 14 (merging passages 93A, 93B, which will be described later). Is supplied / discharged to / from the boom cylinder 8A of the work device 7 via the pressure oil supply / discharge ports 53A, 53B. In this way, the boom control valves 47 and 48 are in a relationship in which the pressure oils from the two hydraulic pumps 77 and 79 merge with each other, and the boom spools 49 and 51 of the boom control valves 47 and 48 are identical to each other. It is provided in the side housing block 14.

  Reference numerals 54 and 55 denote arm direction control valves (hereinafter referred to as arm control valves 54 and 55) provided in the other housing block 14, and one arm control valve 54 of the arm control valves 54 and 55. 11 is constituted by a spool valve in which a first arm spool 56 is inserted into the spool sliding hole 44 as shown in FIG. The arm control valve 54 is located on both sides in the axial direction of the arm spool 56 and has left and right hydraulic pilot portions 54A and 54B in the cover bodies 24 and 25. The right hydraulic pilot portion 54B includes an arm A spring 57 that urges the spool 56 toward the neutral position at all times is provided.

  Here, the arm control valve 54 moves the arm spool 56 in the axial direction of the spool sliding hole 44 according to the pilot pressure supplied to the hydraulic pilot portions 54A and 54B from an operation valve (not shown) such as an arm operation lever. The oil grooves 44A and 44B on the actuator side are selectively communicated and blocked with respect to the oil grooves 44C and 44D on the hydraulic power source side. As a result, the arm control valve 54 is switched from the neutral position (A) in FIG. 14 to the left and right switching positions (B) and (C).

  The other arm control valve 55 out of the arm control valves 54 and 55 is constituted by a spool valve formed by inserting a second arm spool 58 into the spool sliding hole 45. The other arm control valve 55 is located on both axial sides of the arm spool 58 and has left and right hydraulic pilot portions 55A and 55B in the cover bodies 24 and 25. The right hydraulic pilot portion 55B includes A spring 59 is provided to urge the arm spool 58 toward the neutral position at all times.

  Here, similarly to the arm control valve 54 described above, the arm control valve 55 moves the arm spool 58 in the axial direction of the spool sliding hole 45 in accordance with the pilot pressure supplied from the operation valve to the hydraulic pilot portions 55A and 55B. The oil grooves 45A and 45B on the actuator side are selectively communicated and blocked with respect to the oil grooves 45C and 45D on the hydraulic power source side. As a result, the arm control valve 55 is switched from the neutral position (A) in FIG. 14 to the switching position (B), (C), and the pressure oil supply / discharge ports 60A and 60B described later together with the arm control valve 54. The pressure oil is supplied and discharged.

  60A and 60B are pressure oil supply / discharge ports provided on the side surface 14D of the housing block 14, and the pressure oil supply / discharge ports 60A and 60B are connected on the one side via merging passages 94A and 94B described later, as shown in FIG. The oil grooves 44A and 44B on the actuator side and the oil grooves 45A and 45B are communicated with each other, and the other side is opened on the side surface 14D of the housing block 14 as shown in FIG. The pressure oil supply / discharge ports 60A and 60B supply and discharge pressure oil to and from the arm cylinder 9A (see FIG. 1) of the work device 7.

  That is, the arm control valves 54 and 55 merge the pressure oil discharged from the hydraulic pumps 77 and 79 described later in the other side housing block 14 (merging passages 94A and 94B described later). Is supplied / discharged to / from the arm cylinder 9A of the work device 7 via the pressure oil supply / discharge ports 60A, 60B. Thus, the arm control valves 54 and 55 are in a relationship in which the pressure oils from the two hydraulic pumps 77 and 79 merge with each other, and the arm spools 56 and 58 of the arm control valves 54 and 55 are the same It is provided in the side housing block 14.

  Reference numeral 61 denotes a turning direction control valve (hereinafter referred to as a turning control valve 61) provided in the other housing block 14, and the turning control valve 61 is spooled in the spool sliding hole 46 as shown in FIG. The spool valve is formed by inserting 62. The turning control valve 61 has left and right hydraulic pilot portions 61A and 61B in the cover bodies 24 and 25 located on both sides in the axial direction of the spool 62, and the right hydraulic pilot portion 61B includes a spool. A spring 63 that biases 62 toward the neutral position at all times is provided.

  Here, the turning control valve 61 displaces the spool 62 in the axial direction of the spool sliding hole 46 in accordance with the pilot pressure supplied to the hydraulic pilot portions 61A and 61B from an operation valve (not shown) such as a turning operation lever. Then, the oil grooves 46A and 46B on the actuator side are selectively communicated and blocked with respect to the oil grooves 46C and 46D on the hydraulic power source side. Thereby, the turning control valve 61 is switched from the neutral position (A) in FIG. 14 to the switching positions (B) and (C).

  64A and 64B are pressure oil supply / discharge ports provided on the side surface 14C of the housing block 14, and the pressure oil supply / discharge ports 64A and 64B communicate with the oil grooves 46A and 46B on the actuator side as shown in FIG. On the other hand, the side wall 14D of the housing block 14 is opened as shown in FIG. As shown in FIG. 14, the pressure oil supply / discharge ports 64 </ b> A and 64 </ b> B supply and discharge pressure oil to the turning motor 3 </ b> M provided on the upper turning body 3 (see FIG. 1).

  65 is a first pump port provided on the side surface 13C of the one-side housing block 13, and the first pump port 65 is located on the side surface 13C at a position above a cover 81A described later as shown in FIG. It opens to the center and is connected to the discharge side of a hydraulic pump 77 described later. As shown in FIG. 6, the first pump port 65 communicates with a pump passage 66, a center bypass passage 67, high-pressure passages 68 and 69, etc. that are formed in the one-side housing block 13.

  Here, the center bypass passage 67 and the high pressure passage 68 communicate with the first pump port 65 via the pump passage 66 as shown in FIGS. Further, as shown in the hydraulic circuit of FIG. 14, the high-pressure passage 69 is a passage branched from the one-side passage portion 67A of the center bypass passage 67 between the traveling control valve 26 and the bucket control valve 34. The bypass passage 67 is disposed at a position closer to the side surface 13C of the housing block 13 than the one-side passage portion 67A (see FIGS. 6, 8, and 9). As shown in FIG. 6, the center bypass passage 67 and the high-pressure passage 69 are formed to extend upward and downward (Z-axis direction) from the one-side housing block 13 into the other-side housing block 14.

  As shown in FIGS. 6 and 14, the center bypass passage 67 is formed in the one-side housing block 13 and is formed in the first one-side passage portion 67 </ b> A that extends upward and downward and in the other-side housing block 14. The first other-side passage portion 67B extending upward and downward, and a connection port 67C for communicating the passage portions 67A and 67B at the positions of the mating surfaces 13B and 14A are included. By this connection port 67C, the passage portions 67A and 67B of the center bypass passage 67 are liquid-tightly connected above and below the mating surfaces 13B and 14A as shown in FIG.

  The high-pressure passage 69 is formed in the first housing block 13 and extends upward and downward, and the first high-pressure passage 69A is formed in the other housing block 14 and extends upward and downward. The other side passage portion 69B and a connection port 69C for communicating between the passage portions 69A and 69B at the positions of the mating surfaces 13B and 14A. By this connection port 69C, the passage portions 69A and 69B of the high-pressure passage 69 are liquid-tightly connected above and below the mating surfaces 13B and 14A. As shown in FIG. 13, the connection port 67C of the center bypass passage 67 and the connection port 69C of the high pressure passage 69 are provided with four bolts 16 and low pressure side oil passages (that will be described later) provided at the four corners of the other side housing block 14. The side passage portions 70B of the low pressure passage 70 and the side passage portions 76B) of the tank passage 76 are arranged at positions closer to the center of the mating surface 14A.

  Here, the pump passage 66 and the high-pressure passage 69 pass the pressure oil discharged from the first hydraulic pump 77 to the travel control valve 26, the bucket control valve 34, the boom control valve 47, the arm control valve 54, and the like. The high pressure side of the hydraulic source side oil passage to be supplied is configured. As shown in FIG. 14, the one-side passage portion 69A of the high-pressure passage 69 branches from the one-side passage portion 67A of the center bypass passage 67 between the traveling control valve 26 and the bucket control valve 34, as shown in FIG. A first one-side oil passage system in which the downstream side extends to the position of the connection port 69C is configured.

  One side passage portion 69A of the high-pressure passage 69 communicates with the connection port 69C between the mating surfaces 13B and 14A on the upstream side, and the first side passage portion 69A is connected in parallel to the boom control valve 47 and the arm control valve 54. The other side oil passage system is configured. That is, the one-side passage portion 69A of the high-pressure passage 69 is aligned with the mating surfaces 13B, 13B from the position upstream of the bucket control valve 34 (spool 35) disposed near the mating surface 13B of the one-side housing block 13. Pressure oil from the first hydraulic pump 77 is supplied to the first other-side passage portion 69B and the control valves 47 and 54 (spools 49 and 56) through the connection port 69C between 14A.

  70 is a low-pressure passage formed in the one-side housing block 13, and the low-pressure passage 70 is located away from the pump passage 66, the center bypass passage 67, and the high-pressure passages 68 and 69, as shown in FIGS. Is formed. The low-pressure passage 70 includes a plurality (two) of upper passage portions 70A extending along the upper surface 13A of the one-side housing block 13 and upper and left ends of the one-side housing block 13 that communicate with the upper passage portions 70A. The left and right side passage portions 70B extend downward along the side surfaces 13E and 13F.

  Each side passage portion 70B of the low-pressure passage 70 communicates with each side passage portion 76B of the tank passage 76 described later at the position of the mating surface 13B. Therefore, the oil liquid (return oil from each hydraulic actuator) flowing in the upper passage portion 70A and the side passage portion 70B of the low pressure passage 70 is discharged to the tank 78 described later via the tank passage 76. .

  Reference numeral 71 denotes a second pump port provided on the side surface 14C of the other housing block 14, and the second pump port 71 is located on the side surface 14C at a position below a cover 85A described later as shown in FIG. And is connected to the discharge side of a second hydraulic pump 79 described later. The second pump port 71 communicates with a pump passage 72 formed in the other housing block 14 and extends from the other housing block 14 to the one housing block 13, for example, in the Z-axis direction. The center bypass passage 73 and the high pressure passage 74 are also communicated.

  Here, as shown in the hydraulic circuit of FIG. 14, the high pressure passage 74 branches from the pump passage 72 at a position upstream of the turning control valve 61, and the center bypass passage 73 is connected to the pump passage 72 at this branch position. It is connected to the. Further, as shown in FIG. 6, the high pressure passage 74 is disposed at a position closer to the side surfaces 13 </ b> D and 14 </ b> D of the housing blocks 13 and 14 than the center bypass passage 73. The center bypass passage 73 and the high pressure passage 74 are formed to extend upward from the other housing block 14 into the one housing block 13.

  As shown in FIGS. 6 and 14, the center bypass passage 73 is formed in the second housing block 14 and the second first passage portion 73 </ b> A formed in the first housing block 13 and extending upward and downward. The second other passage portion 73B extending upward and downward, and a connection port 73C for communicating between the passage portions 73A and 73B at the positions of the mating surfaces 13B and 14A are configured. By this connection port 73C, the passage portions 73A and 73B of the center bypass passage 73 are liquid-tightly connected above and below the mating surfaces 13B and 14A as shown in FIG.

  The high-pressure passage 74 connected to the second hydraulic pump 79 is formed in the second housing block 14 and the second first passage portion 74A formed in the first housing block 13 and extending upward and downward. A second other passage portion 74B extending in the upward and downward directions and a connection port 74C for communicating between the passage portions 74A and 74B at the positions of the mating surfaces 13B and 14A are configured. By this connection port 74C, the passage portions 74A and 74B of the high-pressure passage 74 are liquid-tightly connected above and below the mating surfaces 13B and 14A as shown in FIG. As shown in FIG. 13, the connection port 73C of the center bypass passage 73 and the connection port 74C of the high pressure passage 74 have four bolts 16 and low pressure side oil passages (that is, low pressure side passages) provided at the four corners of the other side housing block 14. Each side passage portion 70B of the passage 70 and each side passage portion 76B of the tank passage 76 described later are disposed at positions closer to the center side of the mating surface 14A.

  The pump passage 72 and the high-pressure passage 74 are configured to send pressure oil discharged from a second hydraulic pump 79, which will be described later, to the turning control valve 61, the arm control valve 55, the boom control valve 48, the spare control valve 38, and the travel. The high pressure side of the oil pressure source side oil passage supplied to the control valve 30 or the like is configured. The one-side passage portion 74A of the high-pressure passage 74 communicates with the connection port 74C between the mating surfaces 13B and 14A on the upstream side, and is connected in parallel to the spare control valve 38 and the travel control valve 30 on the downstream side. A second one-side oil passage system that supplies pressure oil from the second hydraulic pump 79 to the cylinder 31 is configured.

  As shown in FIG. 14, the other side passage portion 74B of the high pressure passage 74 is located on the upstream side of the turning control valve 61 (the position upstream of the control valve 61). The second other-side oil passage system is branched from the portion 73B and the downstream side extends to the position of the connection port 74C. The downstream side of the other-side passage portion 74B is connected in parallel to the arm control valve 55 and the boom control valve 48, and supplies pressure oil from the second hydraulic pump 79 to the spools 58 and 51.

  In other words, the one-side housing block 13 includes a first one-side oil passage system including a one-side passage portion 69 </ b> A in which the high-pressure sides of the plurality of hydraulic source-side oil passages are connected to the first hydraulic pump 77, and the second The second one-side oil passage system including the one-side passage portion 74A connected to the hydraulic pump 79 is formed separately. The other housing block 14 includes a first other-side oil passage system including an other-side passage portion 69B in which the high-pressure sides of the plurality of oil-source-side oil passages are connected to the first hydraulic pump 77, and a second It is formed separately from the second other-side oil passage system composed of the other-side passage portion 74B connected to the hydraulic pump 79.

  A first one-side oil passage system (one-side passage portion 69A) formed in the one-side housing block 13 is a first other-side oil passage system (other-side passage portion 69B) formed in the other-side housing block 14. Are connected through a connection port 69C between the mating surfaces 13B and 14A. A second one-side oil passage system (one-side passage portion 74A) formed in the one-side housing block 13 is a second other-side oil passage system (other-side passage portion 74B) formed in the other-side housing block 14. Are connected through a connection port 74C between the mating surfaces 13B and 14A.

  75 is a tank port provided on the side surface 14C of the other housing block 14, and the tank port 75 opens to the side surface 14C at a position spaced leftward from the second pump port 71 as shown in FIG. It is connected to a tank 78 described later. The tank passage 76 as a low pressure passage has a lower passage portion 76A and left and right side passage portions 76B as shown in FIGS. The tank port 75 communicates with the left and right side passage portions 76B through the lower passage portion 76A of the tank passage 76, and the oil liquid (return from each hydraulic actuator) that flows in the side passage portions 76B. Oil) is discharged into a tank 78.

  Here, as shown in FIGS. 4 and 5, for example, the side passage portions 76B are formed to be greatly separated from each other in the left and right sides (X-axis direction) in the other-side housing block 14. These side passage portions 76B are liquid-tightly connected to the side passage portions 70B of the low-pressure passage 70 formed in the one-side housing block 13 at the positions of the mating surfaces 13B and 14A. Since the oil liquid (return oil) flowing between the side passage portions 70B and 76B is at a low pressure, there is little oil leakage (leak) at the positions of the mating surfaces 13B and 14A.

  Reference numeral 77 denotes a first hydraulic pump that constitutes a first hydraulic power source together with the tank 78. The discharge side of the first hydraulic pump 77 is connected to the first pump port 65 as shown in FIGS. The pressure oil is supplied to the control valves 26, 34, 47, 54 (spools 27, 35, 49, 56) through the pump passage 66 and the high pressure passage 69.

  Reference numeral 79 denotes a second hydraulic pump that constitutes a second hydraulic power source together with the tank 78. The discharge side of the second hydraulic pump 79 is connected to the second pump port 71 as shown in FIGS. The pressure oil is supplied to the control valves 61, 55, 48, 38, 30 (spools 62, 58, 51, 39, 31) through the pump passage 72 and the high pressure passage 74.

  80 is a check valve attached to the travel control valve 30. The check valve 80 is mounted so as to be inserted from the side surface 13D of the housing block 13 toward the high pressure passage 74 as shown in FIG. Is closed by the cover 80A. The check valve 80 allows pressure oil to flow from the high-pressure passage 74 toward the oil groove 19 </ b> C, and prevents reverse flow.

  81 is a check valve attached to the bucket control valve 34. The check valve 81 is attached so as to be inserted from the side surface 13C of the housing block 13 toward the high pressure passage 69 as shown in FIG. Is closed by a cover 81A. The check valve 81 allows the pressure oil to flow from the high-pressure passage 69 toward the oil groove 20 </ b> C, and prevents a reverse flow.

  Reference numeral 82 denotes another check valve attached to the spare control valve 38. The check valve 82 is configured in substantially the same manner as the above-described check valve 80, and a cover 82A is provided on the side surface 13D side of the housing block 13. The check valve 82 allows the pressure oil to flow from the high-pressure passage 74 toward the oil groove 21 </ b> C, and prevents a reverse flow.

  The other side housing block 14 is also provided with check valves 83 to 87. Among these, the check valves 83 and 84 are attached to the boom control valves 47 and 48 as shown in FIG. 16, and these check valves 83 and 84 are provided with covers 83A and 84A. On the other hand, the check valves 85 and 86 are attached to the arm control valves 54 and 55 as shown in FIG. 11, and these check valves 85 and 86 are provided with covers 85A and 86A. Furthermore, the check valve 87 is attached to the turning control valve 61 as shown in FIG. 12, and the check valve 87 includes a cover 87A.

  88 is a main relief valve provided in the one-side housing block 13, and the relief valve 88 is located between the pair of check valves 89, 90 as shown in FIGS. 9 and 14. Installed on. As shown in FIG. 9, the check valve 89 is always urged in the valve closing direction by the valve spring 89 </ b> A so as to close the relief passage 91 communicating with the high pressure passage 68. When the pressure in the relief passage 91 exceeds the set pressure of the valve spring 89A, the check valve 89 is opened, and the pressure in the high pressure passage 68 is guided to the pressure chamber 88A of the relief valve 88 via the relief passage 91. . However, the check valve 89 prevents the oil liquid from flowing from the pressure chamber 88A toward the relief passage 91 side.

  The check valve 90 is always urged in the valve closing direction by the valve spring 90A so as to close the relief passage 92 communicating with the high pressure passage 74. When the pressure in the relief passage 92 exceeds the set pressure of the valve spring 90A, the check valve 90 opens, and the pressure in the high pressure passage 74 is guided to the pressure chamber 88A of the relief valve 88 through the relief passage 92. . However, the check valve 90 prevents the oil liquid from flowing from the pressure chamber 88A toward the relief passage 92 side.

  The relief valve 88 opens when the pressure in the pressure chamber 88A (that is, the high pressure passages 68 and 74) exceeds a predetermined relief set pressure, and the excess pressure at this time is passed through the side passage portion 70B of the low pressure passage 70 and the like. And relief to the tank 78 side. Thereby, the relief valve 88 suppresses the maximum pressure in the pump passages 66, 72 and the high pressure passages 68, 69, 74 to a predetermined relief setting pressure or less.

  Here, as shown in FIG. 5, the relief valve 88 is provided below the spare control valve 38 (spool sliding hole 21) and close to the mating surface 13B of the housing block 13, that is, in the housing block 13. It is disposed at a position closer to the mating surface 13B than the spool sliding holes 18-21. Thereby, for example, as shown in FIG. 14, the relief valve 88 is located at a substantially intermediate position between the first pump port 65 and the second pump port 71 (that is, the pipe line length between the two is almost equal. Position).

  93A and 93B are merging passages provided between the boom control valves 47 and 48 in the other housing block 14, and the merging passages 93A and 93B are formed as shown in FIG. 42) and the oil grooves 43A and 43B of the boom control valve 48 (spool sliding hole 43) are always in communication. The merge passages 93A and 93B constitute the actuator side oil passages of the boom control valves 47 and 48 together with the oil grooves 42A and 42B and the oil grooves 43A and 43B. The joining passages 93A and 93B join together the pressure oil supplied from the first and second hydraulic pumps 77 and 79 to the boom control valves 47 and 48 (boom spools 49 and 51). The pressure oil supply / discharge ports 53A and 53B are supplied to and discharged from the boom cylinder 8A of the work device 7.

  94A and 94B are merging passages provided between the arm control valves 54 and 55 in the other side housing block 14, and these merging passages 94A and 94B are arm control valves 54 (spool sliding holes as shown in FIG. 11). 44) and the oil grooves 45A, 45B of the arm control valve 55 (spool sliding hole 45) are always in communication. The merging passages 94A and 94B constitute the actuator side oil passages of the arm control valves 54 and 55 together with the oil grooves 44A and 44B and the oil grooves 45A and 45B. The joining passages 94A and 94B join together the pressure oil supplied from the first and second hydraulic pumps 77 and 79 to the arm control valves 54 and 55 (arm spools 56 and 58). The pressure oil supply / discharge ports 60A and 60B are supplied to and discharged from the arm cylinder 9A of the work device 7.

  The multiple valve device 11 mounted on the hydraulic excavator 1 according to this embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when the hydraulic excavator 1 (vehicle) travels, if the operator who has boarded the cab 4 tilts the left and right travel levers, the left and right travel control valves 26 according to the pilot pressure at this time. , 30 are switched from the neutral position (A) to any one of the switching positions (B), (C).

  Thus, the right travel control valve 26 supplies and discharges the pressure oil from the hydraulic pump 77 to the right travel motor 2R via the pressure oil supply / discharge ports 29A and 29B. The left travel control valve 30 supplies and discharges the pressure oil from the hydraulic pump 79 to the left travel motor 2L via the pressure oil supply / discharge ports 33A and 33B. As a result, the lower traveling body 2 can perform a traveling operation in which the crawler belt is driven by the left and right traveling motors 2L and 2R to move the vehicle forward or backward.

  Further, when excavation work such as earth and sand is performed at the work site, the bucket 10 is rotated while the boom 8 and the arm 9 of the working device 7 are moved up and down. That is, when the operator in the cab 4 tilts the bucket operation lever, the bucket control valve 34 is switched from the neutral position (A) to any one of the switching positions (B) and (C). The pressure oil from the hydraulic pump 77 is supplied / discharged to / from the bucket cylinder 10A via the bucket control valve 34 and the pressure oil supply / discharge ports 37A, 37B.

  When the boom control lever is tilted, the boom control valves 47 and 48 are switched from the neutral position (A) to any one of the switching positions (B) and (C). Thus, the pressure oil discharged from the first and second hydraulic pumps 77 and 79 is joined to each other via the joining passages 93A and 93B by the boom control valves 47 and 48, and the joined pressure oil is used as the pressure oil. The boom cylinder 8A can be supplied and discharged via the supply / discharge ports 53A and 53B.

  When the arm operation lever is tilted, the arm control valves 54 and 55 are switched from the neutral position (A) to any one of the switching positions (B) and (C). As a result, the pressure oil discharged from the first and second hydraulic pumps 77 and 79 are joined together by the arm control valves 54 and 55 via the joining passages 94A and 94B, and the joined pressure oil is used as the pressure oil. The arm cylinder 9A can be supplied / discharged via the supply / discharge ports 60A, 60B.

  When the upper swing body 3 is driven to turn on the lower traveling body 2, the turning control valve 61 is moved from the neutral position (A) to the switching position (B) or (C) according to the tilting operation of the turning operation lever. Switch to Thus, the pressure oil discharged from the second hydraulic pump 79 can be supplied to and discharged from the turning motor 3M through the turning control valve 61 and the pressure oil supply / discharge ports 64A and 64B, and the turning motor 3M is driven to turn. can do.

  By the way, when the valve housing 12 'of the multiple valve device 11' is divided into two parts as in the comparative example shown in FIG. 15, the left housing block is divided into two parts in the left and right directions (for example, the Y-axis direction). 13 ', right housing block 14' may be used. The left housing block 13 ′ and the right housing block 14 ′ shown in FIG. 15 abut against each other at positions of mating surfaces 13 B ′ and 14 A ′ extending in the upward and downward directions (Z-axis direction), for example.

  However, in the comparative example shown in FIG. 15, in order to increase the number of spools provided in the left housing block 13 'and the right housing block 14', the size of each housing block 13 ', 14' is increased. Therefore, the area of the mating surfaces 13B 'and 14A' must be increased, and the possibility of occurrence of poor sealing and oil leakage at the positions of the mating surfaces 13B 'and 14A' increases.

  In addition, when the first and second hydraulic pumps 77 and 79 are used as the hydraulic source and the pressure oil from the two hydraulic pumps 77 and 79 is supplied to the boom cylinder 8A and the arm cylinder 9A to be supplied, the boom Between the control valves 47 and 48, the joining passages 93A and 93B are respectively divided into two at the positions of the mating surfaces 13B 'and 14A', and the two are communicated by the connection ports 93A 'and 93B'. Between the arm control valves 54 and 55, the joining passages 94A and 94B are respectively divided into two at the positions of the mating surfaces 13B 'and 14A', and the two are communicated by connection ports 94A 'and 94B'.

  As a result, a total of four connection ports 93A ', 93B', 94A ', 94B' are formed at the positions of the mating surfaces 13B ', 14A' of the housing blocks 13 ', 14'. Further, a connection port 68 ′ is formed at the position of the mating surfaces 13 B ′ and 14 A ′ in the high pressure passage 68 that guides the pressure oil from the first hydraulic pump 77 to the relief valve 88 on the downstream side of the check valve 89. A connection port 72 ′ is also formed at the position of the mating surfaces 13 B ′ and 14 A ′ in the pump passage 72 communicating with the second pump port 71.

  Thus, in the comparative example shown in FIG. 15, a total of six connection ports 68 ′, 72 are provided at the positions of the mating surfaces 13B ′, 14A ′ interposed between the left housing block 13 ′ and the right housing block 14 ′. ', 93A', 93B ', 94A', 94B 'are formed. As a result, the number of pressure oil merging points on the mating surfaces 13B ′ and 14A ′ increases to six, and the possibility of oil leakage increases.

  Therefore, in the first embodiment, in order to solve such a problem, the valve housing 12 of the multiple valve device 11 is moved upward and downward (for example, in the Z-axis direction) from the one-side housing block 13 and the other side. The housing block 14 is divided into two, and the one-side housing block 13 and the other-side housing block 14 are abutted and separated from each other at the positions of the mating surfaces 13B and 14A facing the other side in the upward and downward directions. The configuration is as follows.

  Therefore, a total of four connection ports 67C, 69C, 73C, and 74C are provided at the positions of the mating surfaces 13B and 14A between the one-side housing block 13 and the other-side housing block 14 as shown in FIG. Thus, the pressure oil from the first and second hydraulic pumps 77, 79 is supplied to all the control valves 26, 30, 34, 38, 47, 48, 54, 55, 61 (spools 27, 31, 35, 39, 49). 51, 56, 58, 62), the number of connection ports 67C, 69C, 73C, 74C can be reduced to the minimum necessary, and the occurrence of oil leakage between the mating surfaces 13B, 14A can be suppressed. it can.

  That is, the pressure oil from the first hydraulic pump 77 is supplied to the one-side housing block via the one-side passage portion 67A of the center bypass passage 67 and the one-side passage portion 69A (first one-side oil passage system) of the high-pressure passage 69. 13 can be supplied to the control valves 26 and 34 (spools 27 and 35) in the engine 13, and the pressure oil from the first hydraulic pump 77 can be supplied to the other side passage portion of the other side housing block 14 through the connection port 69C of the mating surfaces 13B and 14A. 69B (first other-side oil passage system) can be supplied to control valves 47 and 54 (spools 49 and 56) in the other-side housing block 14.

  The pressure oil from the second hydraulic pump 79 passes through the other side housing block 14 via the other side passage 73B of the center bypass passage 73 and the other side passage 74B (second other oil passage system) of the high pressure passage 74. Can be supplied to the control valves 61, 55, and 48 (spools 62, 58, and 51), and pressure oil from the second hydraulic pump 79 can be supplied to the one side housing block 13 through the connection port 74C of the mating surfaces 13B and 14A. It can also be supplied to the side passage portion 74A (second one-side oil passage system) and supplied to the control valves 38 and 30 (spools 39 and 31).

  Further, since the boom control valves 47 and 48 (boom spools 49 and 51) for controlling the boom cylinder 8A are provided in the same other side housing block 14, the first and second hydraulic pumps 77 and 79 are used. The discharged pressure oil can be merged in one other housing block 14 (merging passages 93A, 93B) and supplied to the two boom spools 49, 51. For this reason, it is not necessary to provide the merging passages 93A and 93B at a position sandwiching the mating surfaces 13B and 14A of the two housing blocks 13 and 14. On the other hand, for example, in the comparative example shown in FIG. 15, the connection ports 93A 'and 93B' of the merging passages 93A and 93B are provided at the positions of the mating surfaces 13B 'and 14A' of the housing blocks 13 'and 14'. The number is increasing.

  For this reason, in the first embodiment, the number of connection ports on the mating surfaces 13B and 14A can be reduced, and the occurrence of oil leakage or the like can be suppressed. Also, the arm control valves 54 and 55 (arm spools 56 and 58) for controlling the arm cylinder 9A are provided in the same other side housing block 14 so that the first and second hydraulic pumps 77 and 79 are provided. The discharged pressure oil can be merged in one other housing block 14 (merging passages 94A, 94B) and supplied to the two arm spools 56, 58, and the number of connection ports can be reduced.

  In addition, each recessed portion 15 is formed in the one-side housing block 13 to be a seat surface portion 15A for fastening bolts between the mating surface 13B. Thus, when the one-side housing block 13 is fixed (coupled) to the other-side housing block 14 in an abutting state, a plurality of relatively short lengths are provided on the seating surface portion 15A by utilizing the bolt mounting space by the respective recessed portions 15. By simply fastening the bolt 16, the one-side housing block 13 and the other-side housing block 14 can be fixed in an abutting state, and the valve housing 12 of the multiple valve device 11 can be easily assembled. In addition, the fastening positions of the bolts 16 are located on the inner side of the corners of the mating surfaces 13B and 14A of the housing blocks 13 and 14, which is effective in suppressing the occurrence of oil leakage from the mating surfaces 13B and 14A. It becomes composition.

  If the concave recesses 15 are not provided at the four corners of the one-side housing block 13, it is necessary to fasten the two housing blocks using long bolts. The internal spool sliding hole is easily deformed by the tightening force. However, the concave recesses 15 are provided at the four corners of the one-side housing block 13, and the plurality of short bolts 16 are fastened to the seating surface portion 15A, whereby the spool sliding holes 18, 19 in the housing blocks 13, 14 are secured. , 20, 21, 42, 43, 44, 45, 46, and can maintain good slidability of the spools 27, 31, 35, 39, 49, 51, 56, 58, 62. Can do.

  In the one-side housing block 13, for example, a total of four spool sliding holes 18 to 21 extend in parallel with each other along the X-axis direction in a state of being separated from each other in the Y-axis direction and the Z-axis direction. The left and right traveling control valves 26 and 30, the bucket control valve 34, and the spare control valve 38 are assembled in a compact structure on the one side housing block 13 side. be able to. In addition, a relief valve 88 that suppresses the maximum pressure in the pump passage 66 and the high-pressure passages 69 and 74 (hydraulic circuit) to be equal to or lower than a predetermined set pressure can be disposed on the one-side housing block 13 side.

  On the other hand, in the other housing block 14, for example, a total of five spool sliding holes 42 to 46 are separated from each other in the Y-axis direction and the Z-axis direction and extend in parallel to each other in the X-axis direction. It can be arranged with a structure. As a result, the boom control valves 47 and 48, the arm control valves 54 and 55, and the turning control valve 61 can be assembled in a compact structure on the other housing block 14 side.

  Therefore, when the number of spool sliding holes (spool valves) provided in the valve housing 12 is increased, it is only necessary to increase the dimensions of the housing blocks 13 and 14 in the Z-axis direction perpendicular to the mating surfaces 13B and 14A. For example, it is not necessary to increase the size of the housing blocks 13 and 14 in the Y-axis direction parallel to the mating surfaces 13B and 14A, and the area of the mating surfaces 13B and 14A can be made as small as possible.

  Further, the seating surface portion 15A of the four recessed portions 15 has four fastening portions for fixing the one-side housing block 13 and the other-side housing block 14 in an abutting state using four bolts 16. The high-pressure side oil passage (that is, the connection ports 67C, 69C, 73C, and 74C) that is configured and passes through the positions of the mating surfaces 13B and 14A has four fastening portions (seat surface portions 15A, that is, bolts 16) and low-pressure side oil. They are arranged closer to the center of the mating surfaces 13B and 14A than the passages (that is, the side passage portions 70B of the low pressure passage 70 and the side passage portions 76B of the tank passage 76). For this reason, the two housing blocks 13 and 14 can be fastened with the four bolts 16 in a state where they are abutted at the positions of the mating surfaces 13B and 14A, and the connection ports 67C, 69C, 73C and 74C are mated. It can arrange | position in the position near the center side of 13B and 14A. As a result, the connection ports 67C, 69C, 73C, and 74C are connected from the fastening position of each bolt 16 and the low pressure side oil passage (that is, each side passage portion 70B of the low pressure passage 70 and each side passage portion 76B of the tank passage 76). It can arrange | position in the position close | similar to the center, and can suppress that the pressure oil which distribute | circulates connection port 67C, 69C, 73C, 74C leaks outside from the position of the mating surfaces 13B and 14A.

  Therefore, according to the first embodiment, the abutting area between the one-side housing block 13 and the other-side housing block 14, that is, the mating surfaces 13B and 14A, while taking advantage of the two-divided valve housing 12 is used. FIG. 15 shows the number of passages such as high pressure passages 69 and 74 and center bypass passages 67 and 73 passing through the mating surfaces 13B and 14A (that is, the number of connection ports 67C, 69C, 73C and 74C). This can be reliably reduced compared to the comparative example.

  Thereby, generation | occurrence | production of the oil leak in the mating surfaces 13B and 14A between the one side housing block 13 and the other side housing block 14, seal | sticker failure, etc. can be suppressed, and sealing performance can be improved. In addition, the number of bolts 16 used to fasten the one-side housing block 13 and the other-side housing block 14 in an abutting state can be reduced, and the number of parts can be reduced to improve workability during assembly.

  Further, since the spool sliding holes 18 to 21 and 42 to 46 can be arranged in a compact manner by forming a three-dimensional structure in the one side housing block 13 and the other side housing block 14, compared with the conventional two-part type. In addition, the entire valve housing 12 can be reduced in size and weight, and handling and workability during transfer and transfer can be improved. Further, the structure of the mold, particularly the core, used when casting the one-side housing block 13 and the other-side housing block 14 can be simplified, and internal chips can be removed or confirmed after the molding process. Can be easily performed. Moreover, the working time associated with the molding process during casting can be shortened, and workability and productivity can be improved.

  Further, the one side housing block 13 is provided with a relief valve 88 at a position closer to the mating surface 13B than the spool sliding holes 18 to 21, for example. For this reason, among the plurality of pump passages 66 and 72 and the high-pressure passages 69 and 74 formed in the one-side housing block 13 and the other-side housing block 14, for example, a position that is substantially intermediate between the two hydraulic pumps 77 and 79 ( That is, a relief valve 88 that sets the maximum pressure in the pipe line can be disposed at a position close to the mating surfaces 13B and 14A.

  As a result, the maximum pressure in the pipe line between the pump passage 66 and the high-pressure passage 69 connected to the first hydraulic pump 77 and the pump passage 72 and the high-pressure passage 74 connected to the second hydraulic pump 79. Therefore, the discharge pressure (maximum pressure) adjustment operation between the two hydraulic pumps 77 and 79 can be easily performed.

  Next, FIG. 16 shows a second embodiment of the present invention. A feature of the present embodiment is that both the first and second hydraulic pumps are connected to a hydraulic power source side oil passage provided in one housing block. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In the figure, reference numeral 100 denotes a second hydraulic pump employed in the second embodiment, and the second hydraulic pump 100 is coupled with a tank 78 in the same manner as the hydraulic pump 79 described in the first embodiment. 2 hydraulic sources. However, in this case, the discharge side of the second hydraulic pump 100 is connected to a second pump port 101 which will be described later, and the control valves 30, 38, 48, 55, 61 are connected via the pump passage 102, the high pressure passage 103, and the like. Etc. to supply pressure oil.

  Reference numeral 101 denotes a second pump port provided in the one-side housing block 13. The second pump port 101 is a second hydraulic pump in place of the second pump port 71 described in the first embodiment. 100 is connected to the discharge side. The second pump port 101 communicates with a pump passage 102 formed in the one-side housing block 13 and extends from the one-side housing block 13 to the other-side housing block 14, for example, in an upward or downward direction. The high pressure passage 103 and the center bypass passage 104 are also communicated.

  Here, the second pump port 101 and the pump passage 102 are formed in the one-side housing block 13 so as to be separated from the first pump port 65 and the pump passage 66 in the left and right directions. Further, the high pressure passage 103 and the center bypass passage 104 are also formed so as to be spaced apart from the center bypass passage 67 and the high pressure passage 69 in the left and right directions.

  The high pressure passage 103 branches from the pump passage 102 at a position upstream of the turning control valve 61, and the pressure oil from the second hydraulic pump 100 (that is, the pump passage 102) further branches from the high pressure passage 103. Is supplied to the turning control valve 61 through the center bypass passage 104, and is also supplied to the arm control valve 55, the boom control valve 48, the spare control valve 38, and the traveling control valve 30. The high-pressure passage 103 is formed in the one-side housing block 13 and has a second one-side passage portion 103A that extends upward and downward, and a second one-side passage portion 103A that is formed in the other-side housing block 14 and extends upward and downward. The other side passage portion 103B and a connection port 103C for communicating between the passage portions 103A and 103B at the positions of the mating surfaces 13B and 14A are configured. By this connection port 103C, the passage portions 103A and 103B of the high-pressure passage 103 are liquid-tightly connected above and below the mating surfaces 13B and 14A as shown in FIG.

  The center bypass passage 104 is formed in the one-side housing block 13 and extends upward and downward, and is formed in the other-side housing block 14 and extends upward and downward. The second other-side passage portion 104B is configured to include a connection port 104C that communicates between the passage portions 104A and 104B at the positions of the mating surfaces 13B and 14A. With this connection port 104C, the passage portions 104A and 104B of the center bypass passage 104 are liquid-tightly connected above and below the mating surfaces 13B and 14A as shown in FIG.

  In the second embodiment, the passage 104B of the center bypass passage 104 is connected to the passage 103B of the high-pressure passage 103 in the other housing block 14, and the pressure oil discharged from the second hydraulic pump 100 is high-pressure. The passage 103 is guided from the passage portion 103B side into the passage portion 104B of the center bypass passage 104. Thereafter, when all of the control valves 61, 55, 48, 38, 30 are in the neutral position (A), the inside of the passage portion 104A is connected to the passage portion 104B of the center bypass passage 104 through the connection port 104C between the mating surfaces 13B, 14A. The pressure oil is guided to the bottom and is returned to the tank 78 from the tank passage 76 via the upper passage portion 70A and the side passage portion 70B of the low pressure passage 70.

  The pump passage 102 and the high-pressure passage 103 use the hydraulic oil discharged from the second hydraulic pump 100 to drive the traveling control valve 30, the spare control valve 38, the boom control valve 48, the arm control valve 55, and the turning control. It constitutes the high pressure side of the oil pressure source side oil passage supplied to the valve 61 and the like. The one-side passage portion 103A of the high-pressure passage 103 is connected in parallel to the traveling control valve 30 and the spare control valve 38 to supply the pressure oil from the second hydraulic pump 100 to the spools 31 and 39, and the downstream side thereof A second one-side oil passage system communicating with the connection port 103C between the mating surfaces 13B and 14A is configured.

  The other side passage portion 103B of the high-pressure passage 103 communicates with the connection port 103C between the mating surfaces 13B and 14A on the upstream side, and on the downstream side with the boom control valve 48, the arm control valve 55, and the turning control valve 61. A second other-side oil passage system that supplies pressure oil from the second hydraulic pump 100 to the spools 51, 58, and 62 is connected in parallel.

  In other words, the one-side housing block 13 includes a first one-side oil passage system including a one-side passage portion 69 </ b> A in which the high-pressure sides of the plurality of hydraulic source-side oil passages are connected to the first hydraulic pump 77, and the second It is formed separately from a second one-side oil passage system consisting of one-side passage portion 103A connected to the hydraulic pump 100. The other housing block 14 includes a first other-side oil passage system including an other-side passage portion 69B in which the high-pressure sides of the plurality of oil-source-side oil passages are connected to the first hydraulic pump 77, and a second It is formed separately from the second other-side oil passage system composed of the other-side passage portion 103B connected to the hydraulic pump 100.

  A first one-side oil passage system (one-side passage portion 69A) formed in the one-side housing block 13 is a first other-side oil passage system (other-side passage portion 69B) formed in the other-side housing block 14. Are connected through a connection port 69C between the mating surfaces 13B and 14A. A second one-side oil passage system (one-side passage portion 103A) formed in the one-side housing block 13 is a second other-side oil passage system (other-side passage portion 103B) formed in the other-side housing block 14. Are connected through a connection port 103C between the mating surfaces 13B and 14A.

  Thus, in the second embodiment configured as described above, the pressure oil from the second hydraulic pump 100 is supplied to the control valves 30 and 38 (spools 31 and 39) in the one-side housing block 13. While being able to supply through the side oil passage system (one side passage portion 103A), the pressure oil from the second hydraulic pump 100 is supplied to the second other side of the other side housing block 14 through the connection port 103C between the mating surfaces 13B and 14A. It can be supplied to the side oil passage system (other side passage portion 103B), and the same effect as in the first embodiment can be obtained.

  That is, the first and second connection ports 67C, 69C, 103C, and 104C are provided at the positions of the mating surfaces 13B and 14A between the one-side housing block 13 and the other-side housing block 14 only by providing a total of four connection ports 67C, 69C, 103C, 104C. Pressure oil from the hydraulic pumps 77, 100 of all the control valves 26, 30, 34, 38, 47, 48, 54, 55, 61 (spools 27, 31, 35, 39, 49, 51, 56, 58, 62), the number of connection ports 67C, 69C, 103C, 104C can be reduced to the minimum necessary, and the occurrence of oil leakage between the mating surfaces 13B, 14A can be suppressed.

  In each of the above embodiments, the left and right traveling control valves 26 and 30, the bucket control valve 34, and the spare control valve 38 are provided in the one side housing block 13. The case where the boom control valves 47 and 48, the arm control valves 54 and 55, and the turning control valve 61 are provided has been described as an example. However, the present invention is not limited to this. For example, the one side housing block 13 is provided with two boom control valves, two arm control valves, and one turning control valve. It is good also as a structure which provides the control valve for driving | running | working left, the control valve for driving | running | working right, the control valve for buckets, a backup control valve, etc.

  In this case, the one side housing block 13 is provided with a minimum of three spool sliding holes (for example, a total of three spool sliding holes including a boom control valve, an arm control valve, and a turning control valve), Similarly, the other housing block 14 is provided with a minimum number of three spool sliding holes (for example, a total of three spool sliding holes including a travel left control valve, a travel right control valve, and a bucket control valve). It is good. Specifically, among valve housings provided with 6 to 12 spool sliding holes, 3 to 6 spool sliding holes are provided in one side housing block, and 3 to 6 are provided in the other side housing block. It is good also as a structure which provides an individual spool sliding hole.

  A multiple valve device is mounted to determine which of these control valves (a plurality of control valves composed of 6 to 12 spool sliding holes) is provided in which one of the housing blocks. What is necessary is just to change suitably in relation to a hydraulic excavator (construction machine) or other hydraulic working machines. In this case, the one side housing block is provided with 3 to 6 spool sliding holes so as to form a three-dimensional structure, and the other side housing block is provided with 3 to 6 spool slides so as to form another three-dimensional structure. What is necessary is just to set it as the structure which provides a moving hole.

  The construction machine on which the multiple valve device of the present invention is mounted is not limited to a hydraulic excavator, and can be applied to, for example, a work vehicle called a wheeled hydraulic excavator, a hydraulic crane, a wheel loader, a bulldozer, or a lift truck. Furthermore, it can be applied to hydraulic devices other than construction machines.

1 Excavator (construction machine)
2 Lower traveling body 3 Upper swing body 7 Working device 8 Boom 8A Boom cylinder 9 Arm 9A Arm cylinder 10 Bucket (working tool)
DESCRIPTION OF SYMBOLS 11 Multiple valve apparatus 12 Valve housing 13 One side housing block 13B, 14A Matching surface 14 Other side housing block 15 Recessed part 15A Seat surface part (fastening part)
16 Bolt 17 Screw hole 18, 19, 20, 21 Spool sliding hole 18A, 18B, 19A, 19B, 20A, 20B, 21A, 21B Pressure oil supply / discharge side oil groove (actuator side oil passage)
18C, 19C, 20C, 21C High pressure side oil groove (hydraulic power source side oil passage)
18D, 19D, 20D, 21D Low pressure side oil groove (hydraulic source side oil passage)
22, 23, 24, 25 Cover body 26, 30 Travel control valve 27, 31, 35, 39 Spool 29A, 29B, 33A, 33B, 37A, 37B, 41A, 41B Pressure oil supply / discharge port (actuator side oil passage)
34 Bucket control valve (work implement control valve)
38 Spare control valve 42, 43, 44, 45, 46 Spool sliding hole 42A, 42B, 43A, 43B, 44A, 44B, 45A, 45B, 46A, 46B Oil groove on the pressure oil supply / discharge side (actuator side oil passage) )
42C, 43C, 44C, 45C, 46C High pressure side oil groove (hydraulic source side oil passage)
42D, 43D, 44D, 45D, 46D Low pressure side oil groove (hydraulic source side oil passage)
47, 48 Boom control valve 49, 51 Boom spool 53A, 53B, 60A, 60B, 64A, 64B Pressure oil supply / discharge port (actuator side oil passage)
54, 55 Arm control valve 56, 58 Arm spool 61 Swing control valve 62 Spool 65 First pump port 67, 73, 104 Center bypass passage 67C, 69C, 73C, 74C, 103C, 104C Connection port 68, 69 , 74, 103 High pressure passage (hydraulic source side oil passage)
69A One side passage part (first one side oil passage system)
69B Other side passage part (first other side oil passage system)
70 Low pressure passage (hydraulic source side oil passage)
71, 101 Second pump port 74A, 103A One side passage part (second one side oil passage system)
74B, 103B Other side passage part (second other side oil passage system)
75 Tank port 76 Tank passage (hydraulic source side oil passage)
77 First hydraulic pump (first hydraulic source)
78 Tank 79,100 Second hydraulic pump (second hydraulic source)
80 to 87 Check valve 88 Relief valve 93A, 93B, 94A, 94B Merge passage

Claims (9)

A valve housing provided with six or more spool sliding holes communicating with the plurality of hydraulic source side oil passages and the plurality of actuator side oil passages, and inserted into the respective spool sliding holes of the valve housing. Six or more spools that communicate and block the hydraulic source side oil passage and the actuator side oil passage, and the flow of pressure oil by two hydraulic sources including the first and second hydraulic pumps, In the multiple valve device configured to control using a plurality of spools,
The valve housing includes a one-side housing block having three or more spools that are abutted and separated from each other at the position of the facing mating surfaces, and another housing block having the remaining three or more spools. The structure is divided into two,
The first hydraulic pump is provided in connection with the hydraulic source side oil passage provided in either one of the one side and other side housing blocks,
Pressure oil from the first hydraulic pump is provided in the other housing block through the mating surface from a position upstream of the spool disposed in a position near the mating surface in the one housing block. It is configured to be supplied to a part of the plurality of spools,
The second hydraulic pump is connected to the hydraulic source side oil passage provided in the other housing block of the one side and other side housing blocks,
Pressure oil from the second hydraulic pump is provided to the one housing block through the mating surface from a position upstream of the spool disposed at a position close to the mating surface in the other housing block. Further, the multiple valve device is configured to be supplied to a part of the plurality of spools. A valve housing provided with six or more spool sliding holes communicating with the plurality of hydraulic source side oil passages and the plurality of actuator side oil passages, and inserted into the respective spool sliding holes of the valve housing. Six or more spools that communicate and block the hydraulic source side oil passage and the actuator side oil passage, and the flow of pressure oil by two hydraulic sources including the first and second hydraulic pumps, In the multiple valve device configured to control using a plurality of spools,
The valve housing includes a one-side housing block having three or more spools that are abutted and separated from each other at the position of the facing mating surfaces, and another housing block having the remaining three or more spools. The structure is divided into two,
The first hydraulic pump is provided in connection with the hydraulic source side oil passage provided in either one of the one side and other side housing blocks,
Pressure oil from the first hydraulic pump is provided in the other housing block through the mating surface from a position upstream of the spool disposed in a position near the mating surface in the one housing block. It is configured to be supplied to a part of the plurality of spools,
The second hydraulic pump is a hydraulic source side oil different from the hydraulic source side oil passage to which the first hydraulic pump is connected among the plurality of hydraulic source side oil passages provided in the one housing block. Connected to the aisle,
Pressure oil from the second hydraulic pump is provided to the other housing block through the mating surface from a position upstream of the spool disposed at a position close to the mating surface in the one housing block. In addition, the multiple valve device is configured to be supplied to a spool different from a part of the plurality of spools. The one housing block includes a first one-side oil passage system that connects the plurality of hydraulic source-side oil passages to the first hydraulic pump, and a second one side that is connected to the second hydraulic pump. Formed separately from the oil passage system,
The other housing block includes a first other-side oil passage system that connects the plurality of oil-source-side oil passages to the first hydraulic pump, and a second other side that is connected to the second hydraulic pump. Formed separately from the oil passage system,
The first one-side oil passage system formed in the one housing block is configured to communicate with the first other-side oil passage system formed in the other housing block through the mating surface,
The second one-side oil passage system formed in the one housing block communicates with the second other-side oil passage system formed in the other housing block through the mating surface. The multiple valve device according to 1 or 2. A valve housing provided with six or more spool sliding holes communicating with the plurality of hydraulic source side oil passages and the plurality of actuator side oil passages, and inserted into the respective spool sliding holes of the valve housing. Six or more spools that communicate and block the hydraulic source side oil passage and the actuator side oil passage, and the flow of pressure oil by two hydraulic sources including the first and second hydraulic pumps, In the multiple valve device configured to control using a plurality of spools,
The valve housing includes a one-side housing block having three or more spools that are abutted and separated from each other at the position of the facing mating surfaces, and another housing block having the remaining three or more spools. The structure is divided into two,
The one-side housing block includes a first one-side oil passage system that connects the plurality of hydraulic source-side oil passages to the first hydraulic pump, and a second one side that is connected to the second hydraulic pump. Formed separately from the oil passage system,
The other-side housing block includes a first other-side oil passage system that connects the plurality of oil-source-side oil passages to the first hydraulic pump, and a second other side that is connected to the second hydraulic pump. Formed separately from the oil passage system,
The first one-side oil passage system formed in the one-side housing block is configured to communicate with the first other-side oil passage system formed in the other-side housing block through the mating surface,
The second one-side oil passage system formed in the one-side housing block is configured to communicate with the second other-side oil passage system formed in the other-side housing block through the mating surface. A featured multiple valve device. The first one-side oil passage system is configured such that the pressure oil from the first hydraulic pump is located upstream of the spool disposed at a position close to the mating surface in the one-side housing block. A configuration to supply the first other oil passage system of the other housing block through the mating surface;
The second other-side oil passage system is configured such that the pressure oil from the second hydraulic pump is located upstream of the spool disposed at a position near the mating surface in the other-side housing block. 5. The multiple valve device according to claim 4, wherein the multiple valve device is configured to be supplied to the second one-side oil passage system of the one-side housing block through a mating surface. The first one-side oil passage system is configured such that the pressure oil from the first hydraulic pump is located upstream of the spool disposed at a position close to the mating surface in the one-side housing block. A configuration to supply the first other oil passage system of the other housing block through the mating surface;
The second one-side oil passage system is configured so that the pressure oil from the second hydraulic pump is located upstream of the spool disposed at a position near the mating surface in the one-side housing block. The multiple valve device according to claim 4, wherein the multiple valve device is configured to be supplied to the second other-side oil passage system of the other-side housing block through a mating surface. Either one of the one-side housing block and the other-side housing block is formed by cutting out the four corner portions of the housing block, and a seat surface portion for fastening bolts is formed between the mating surfaces. The four recessed portions are provided, and the seating surface portions of the four recessed portions are four for fixing the one-side housing block and the other-side housing block in an abutting state using a plurality of bolts. The fastening part of
Among the plurality of hydraulic source side oil passages, a high pressure side oil passage connected to the first hydraulic pump or the second hydraulic pump and passing through the position of the mating surface is located at a position closer to the center side of the mating surface. The multiple valve apparatus according to claim 1, 2, 3, 4, 5 or 6, wherein the multiple valve apparatus is arranged.   The two spools having a relationship in which the supplied pressure oils merge with each other among the plurality of spools are provided in the same housing block on one side of the one side and other side housing blocks. , 3, 4, 5, 6 or 7.   The valve housing constitutes a plurality of directional control valves used for a construction machine together with the spools that are respectively inserted and fitted in the spool sliding holes, and the supplied pressure oils of the spools are mutually connected. The two spools in a merged relationship are provided to control the first boom spool and the second boom spool provided to control the boom cylinder of the construction machine or the arm cylinder. The multiple valve device according to claim 1, 2, 3, 4, 5, 6, 7 or 8, comprising a spool for the first arm and a spool for the second arm.

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