CN212838660U

CN212838660U - Multi-way control valve

Info

Publication number: CN212838660U
Application number: CN201720091546.1U
Authority: CN
Inventors: 郇庆祥; 袁青照; 李合永; 张海洋; 巩秀江; 刘桂芳
Original assignee: Shandong Changlin Machinery Group Co Ltd
Current assignee: Shandong Changlin Machinery Group Co Ltd
Priority date: 2017-01-22
Filing date: 2017-01-22
Publication date: 2021-03-30
Anticipated expiration: 2027-01-22

Abstract

The utility model discloses a multiple control valve contains: the first valve body, the second valve body and the third valve body are sequentially communicated, the second valve body comprises two oil return ports, the two oil return ports are communicated with the oil tank, the first valve body and the third valve body, when the multi-way control valve works, return oil of the first valve body and return oil of the third valve body to the oil tank through the oil return ports, the control over the action of engineering machinery is achieved, and particularly different requirements of each execution mechanism of a 40-80 ton hydraulic excavator on flow pressure can be met.

Description

Multi-way control valve

Technical Field

The present invention relates to a multi-way control valve, and more particularly, to a multi-way control valve capable of meeting different requirements of each actuator of a 40-80 ton hydraulic excavator on flow pressure.

Background

With the development of the size increase of hydraulic excavators, the technology of a multi-way control valve, which is one of the key elements of an excavator hydraulic system, has been advanced along with the development of hydraulic excavators. The existing multi-way control valve mostly adopts two valve bodies which are connected in parallel, but in the using process, the power loss is correspondingly increased along with the increase of the total power, because the pressure loss in the multi-way control valve is closely related to the area of the throttling ports, if the pressure loss is reduced, the overflowing area of the throttling ports is increased or the number of the throttling ports is increased, the diameter of the valve core is inevitably increased, so the requirements of the quality, the tightness and the coaxiality of the valve core and the valve hole are difficult to ensure, meanwhile, the existing multi-way control valve is difficult to meet the requirements of a 40-80 ton hydraulic excavator, and the movable arms, the bucket rods, the buckets, the rotary excavator and the left-right walking of each working mechanism can be matched unreasonably in the aspects of pressure flow. It is therefore highly desirable to develop a multiple control valve that overcomes the above-mentioned drawbacks.

SUMMERY OF THE UTILITY MODEL

The present disclosure is intended to provide a simplified summary of the disclosure in order to provide a basic understanding to the reader of the disclosure. This summary is not an extensive overview of the disclosure, and is intended to neither identify key/critical elements of the embodiments nor delineate the scope of the embodiments.

The utility model aims at providing a multiple control valve contains: the multi-way control valve sequentially communicates with a first valve body, a second valve body and a third valve body, the second valve body comprises two oil return ports, the two oil return ports are communicated with an oil tank, the first valve body and the third valve body, and when the multi-way control valve works, return oil of the first valve body and the third valve body flows back to the oil tank through the oil return ports.

The first valve body comprises a left walking link V5, a movable arm second link V4, a rotation link V3, a standby link V2 and an arm first link V1 which are sequentially communicated, and the third valve body comprises a straight walking link V10, a right walking link V9, a movable arm first link V8, a bucket link V7 and an arm second link V6 which are sequentially communicated.

In the above multi-path control valve, the second valve body includes an arm regeneration valve V13 and a boom back pressure valve V12.

The multi-way control valve further comprises a bypass valve, and the first valve body and the third valve body are communicated with the arm second coupling V6 and the arm first coupling V1.

In the above multi-way control valve, the second valve body further comprises two rotary oil supply ports, and the two rotary oil supply ports are communicated with the double rotary motors.

In the above multi-way control valve, the first valve body includes a first oil inlet, and the second valve body includes a second oil inlet.

In the multi-way control valve, the hydraulic oil of the front pump flows to the left traveling block V5 through the first oil inlet and/or the hydraulic oil of the rear pump flows to the right traveling block V9 through the second oil inlet.

In the multi-way control valve, the hydraulic oil of the front pump flows to the rotary union V3 through the first oil inlet P1.

In the multi-way control valve, the hydraulic oil of the front pump flows to the backup link V2 through the first oil inlet P1.

In the multi-way control valve, the hydraulic oil of the rear pump flows to the bucket linkage V7 through the second oil inlet P2.

In the multi-path control valve, the front pump hydraulic oil flows to the first bucket arm linkage V1 through the first oil inlet P1, the rear pump hydraulic oil flows to the second bucket arm linkage V6 through the second oil inlet, and when the two hydraulic oil flows together with the front pump hydraulic oil, the rear pump hydraulic oil sequentially passes through the second valve body and the first valve body and then flows into the bucket cylinder.

In the multi-way control valve, the front pump hydraulic oil flows to the arm first link V1 through the first oil inlet P1, and the rear pump hydraulic oil flows to the arm second link V6 through the second oil inlet P2.

In the multi-path control valve, when the front pump hydraulic oil flows to the second boom linkage V4 through the first oil inlet P1, the rear pump hydraulic oil flows to the first boom linkage V8 through the second oil inlet P2, and when the valves are combined internally, the front pump hydraulic oil flows into the boom cylinder together with the rear pump hydraulic oil after passing through the second valve body and the third valve body in sequence.

When the bucket linkage V7, the boom second linkage V4, and the boom first linkage V8 work simultaneously, the front pump hydraulic oil flows into the boom cylinder after passing through the first oil inlet P1 to the boom second linkage V4, the rear pump hydraulic oil flows into the boom cylinder after passing through the second oil inlet P2 to the boom first linkage V8, and the rear pump hydraulic oil further flows into the bucket linkage V7 through the throttle check valve.

In the multi-way control valve, when the arm second link V6, the boom second link V4 and the boom first link V8 operate simultaneously, the front pump hydraulic oil flows from the first oil inlet P1 to the boom second link V4, and the rear pump hydraulic oil flows from the second oil inlet P2 to the boom first link V8.

The utility model aims at the prior art, and has the advantages that the multi-way control valve adopts an integral structure, has compact structure, and meets different requirements of each actuating mechanism of the excavator on flow pressure; the movable arm confluence and the bucket rod confluence are adopted, and the interior of the valve body is subjected to division and confluence and is distributed to each group of valve cores, so that the flow required by each actuating element is met, the working efficiency is improved, and the labor intensity of an operator is reduced. The system is additionally provided with a boosting loop, when a boosting switch is pressed down, the controller enables the electromagnetic valve to act, the set overflow pressure of the main overflow valve is increased from 34.3Mpa to 37.3Mpa, and the excavating force of the excavator can be instantly increased by 8%. Can carry out the dipper simultaneously and withdraw and the gyration, improve work efficiency. A regeneration function: the dipper has regeneration function, and when the dipper withdrawed the action, the hydraulic oil in dipper loculus can regenerate the dipper vestibule, reduces the energy consumption when improving the efficiency, the utility model discloses a multichannel control valve realizes the control to the engineering machine tool action and especially can satisfy the different demands of each actuating mechanism of 40-80 tons hydraulic shovel to flow pressure.

Drawings

FIG. 1 is a schematic structure diagram of a multi-way control valve of the present invention;

FIG. 2 is a schematic diagram of the left walking couple V5;

FIG. 3 is a schematic diagram of the operation of the swing link V3;

FIG. 4 is a schematic diagram of the operation of the backup gang V2;

FIG. 5 is a schematic diagram of the operation of the bucket hitch V7;

FIG. 6 is a schematic diagram of the operation of the interflow inside the bucket rod coupling;

FIG. 7 is a schematic diagram of the operation of the external confluence of the bucket rod coupling;

FIG. 8 is a schematic diagram of the operation of single straight walking;

FIG. 9 is a schematic diagram of the operation of the boom;

FIG. 10 is a schematic diagram of the operation of the compound linear walking and rotation actions;

FIG. 11 is a schematic diagram of the combined operation of the boom and the bucket;

FIG. 12 is a schematic diagram of the operation of the combined boom and stick operation;

FIG. 13 is a schematic diagram of boom regeneration operation;

FIG. 14 is a schematic diagram of bucket merge operation;

FIG. 15 is a schematic diagram of the pressurization operation of the main spill valve.

Detailed Description

In order to further disclose the features and technical contents of the present invention, please refer to the following detailed description and accompanying drawings, which are provided for reference and illustration purposes only and are not intended to limit the present invention.

Referring to fig. 1, fig. 1 is a schematic structural diagram of a multi-way control valve of the present invention. As shown in fig. 1, the multi-way control valve of the present invention comprises: communicate first valve body T1, second valve body T2 and third valve body T3 in proper order, second valve body T2 contains two oil return ports R1, R2, two oil return ports R1, R2 communicate in the oil tank first valve body T1 and third valve body T3, work as when the multichannel control valve during operation, first valve body T1 and the oil return of third valve body T3 is through oil return port R1, R2 flow back to the oil tank.

Further, the first valve body T1 includes a left travel link V5, a boom second link V4, a swing link V3, a backup link V2, and an arm first link V1, which are sequentially communicated; the third valve body T3 comprises a straight-line walking link V10, a right walking link V9, a movable arm first link V8, a bucket link V7 and an arm second link V6 which are sequentially communicated; the second valve body T2 includes an arm regeneration valve V13 connected to the arm first link V1 and the swing oil replenishment port Rs1 through a casting oil passage, and a boom back pressure valve V12 connected to the boom first link V8 and the oil replenishment port R1 through a casting oil passage. When the arm is internally received, hydraulic oil in the small cavity of the arm returns through the first arm V1 and the arm regeneration valve V13; when the boom descends, the hydraulic oil in the boom large cavity returns through the boom first link V8 and the boom back pressure valve V12.

Still further, the first valve body T1 and the third valve body T3 further include bypass valves V11 and V14, respectively, and the two bypass valves V11 and V14 communicate the arm second link V6 and the arm first link V1.

Furthermore, the second valve body T2 further includes two rotary oil replenishing ports Rs1 and Rs2, and the two rotary oil replenishing ports Rs1 and Rs2 are communicated with the double-rotary motor; the first valve body T1 includes a first oil inlet P1 and the second valve body T2 includes a second oil inlet P2.

The aforementioned components, the oil return port and the rotary oil supply port are connected by at least one oil passage, and the connection mode thereof belongs to the common general knowledge in the art and is not described herein again.

Referring to fig. 2, fig. 2 is a schematic diagram of the left walking couple V5. As shown in fig. 2, the valve core of the left walking link V5 is reversed, and the front pump hydraulic oil enters the walking motor M1 connected with the left walking link V5 after passing through the first oil inlet P1 to the left walking link V5 to realize the left walking function; or the valve core of the right walking link V9 is reversed, and then the hydraulic oil of the pump enters the walking motor (not shown) connected with the right walking link V9 after passing through the second oil inlet P2 to the right walking link V9, so that the right walking function is realized.

Referring to fig. 3, fig. 3 is a schematic diagram of the rotation joint V3. As shown in fig. 3, hydraulic oil of a valve core reversing front pump of the rotary union V3 enters the rotary motor M2 connected with the rotary union V3 after passing through the first oil inlet P1 to the rotary union V3, so that a left-right rotary function is realized.

Referring to fig. 4, fig. 4 is a schematic diagram of the operation of the backup link V2. As shown in fig. 4, the valve core of the backup union V2 is reversed, and the hydraulic oil of the front pump enters the mechanical device connected with the backup union V2 after passing through the first oil inlet P1 to the backup union V2, so as to realize the corresponding function of the mechanical device, wherein in this embodiment, the mechanical device is a breaking hammer, but the utility model discloses do not use this as the limit.

Referring to fig. 5, fig. 5 is a schematic diagram of the operation of the bucket hitch V7. As shown in fig. 5, the valve core of the bucket joint V7 is reversed, and the rear pump hydraulic oil enters the bucket cylinder G1 connected with the bucket joint V7 after passing through the second oil inlet P2 to the bucket joint V7; meanwhile, the bucket oil cylinder G1 realizes oil return through the bucket linkage V7 and the oil port.

Referring to fig. 6, fig. 6 is a schematic diagram of the working principle of the interflow inside the arm linkage. As shown in fig. 6, when front pump hydraulic oil flows to the arm first coupling V1 through the first oil inlet P1, rear pump hydraulic oil flows to the arm second coupling V6 through the second oil inlet P2, and when the valves are subjected to internal confluence, the rear pump hydraulic oil sequentially passes through an oil passage between the second valve body T2 and the first valve body T1 and then flows into the arm oil cylinder G2 connected with the first coupling V1 together with the front pump hydraulic oil, so that an internal confluence function of the valves is realized; the oil returned by the arm cylinder G2 enters the second valve body T2 through the first arm linkage V1 and the bypass valve V11.

Referring to fig. 7, fig. 7 is a schematic diagram of the operation of the outer confluence of the bucket rod coupling. As shown in fig. 7, the front pump hydraulic oil flows from the first oil inlet P1 to the first arm coupling V1, the rear pump hydraulic oil flows from the second oil inlet P2 to the second arm coupling V6, the multi-way control valve further includes an external pipeline W1, the external pipeline is communicated with W1, the second arm coupling V6 and the arm cylinder G2, and when the valves are combined externally, the rear pump hydraulic oil flows into the arm cylinder G2 connected to the first arm coupling V1 together with the front pump hydraulic oil through the external pipeline W1, so that an external valve combining function is realized.

It should be noted that, the inner valve confluence is mainly used for 30-50T excavator, because its working flow is small, and the outer valve confluence is mainly used for 50-80T excavator, because its working flow is large, the outer confluence can reduce pressure loss, but the present invention is not limited thereto.

Referring to fig. 8, fig. 8 is a schematic diagram of the single linear walking operation. As shown in fig. 8, the valve core of the left traveling block V5 is reversed, and the hydraulic oil of the front pump enters the traveling motor M1 connected with the left traveling block V5 after reaching the left traveling block V5 through the first oil inlet P1 to realize the left traveling function; the valve core of the right walking pair V9 is reversed, then hydraulic oil of the rear pump enters a walking motor M3 connected with the right walking pair V9 after passing through a second oil inlet P2 to the right walking pair V9 to realize the right walking function, and oil paths of the left walking pair V5 and the right walking pair V9 are not interfered with each other, so that linear walking is realized.

Referring to fig. 9, fig. 9 is a schematic diagram of the operation of the boom. As shown in fig. 9, when the front pump hydraulic oil flows to the second boom linkage V4 through the first oil inlet P1 and the rear pump hydraulic oil flows to the first boom linkage V8 through the second oil inlet P2, and the valve interior is converged, the front pump hydraulic oil sequentially passes through the second valve body and the third valve body and then flows together with the rear pump hydraulic oil into the first boom linkage V8 to connect the boom cylinder G3 to the first boom linkage V8.

Referring to fig. 10, fig. 10 is a schematic diagram of the operation of the compound actions of linear walking and rotation. As shown in fig. 10, the linear travel link V10 operates in the left position during the left-right travel and rotation operations. At the moment, the hydraulic oil of the front pump simultaneously flows into the left walking pair V5 and the right walking pair V9 through a first oil inlet P1 and then respectively flows into the walking motors M1 and M3, so that the synchronous action of the left walking motor and the right walking motor is realized; the rear pump hydraulic oil flows into the rotary motor M2 after passing through the second oil inlet P2 to the rotary joint V3.

Referring to fig. 11, fig. 11 is a schematic diagram illustrating the operation of the combined operation of the boom and the bucket. As shown in fig. 11, when the bucket linkage V7, the boom second linkage V4, and the boom first linkage V8 work simultaneously, the front pump hydraulic oil flows into the boom cylinder G3 after passing through the first oil inlet P1 to the boom second linkage V4, the rear pump hydraulic oil flows into the boom cylinder G3 after passing through the second oil inlet P2 to the boom first linkage V8, and the rear pump hydraulic oil flows into the bucket cylinder G1 after passing through a throttle check valve (not shown) to the bucket linkage V7. The throttling of the oil inlet of the bucket linkage V7 ensures that the oil inlet hydraulic pressure of the throttling opening of the bucket linkage V7 is the highest pressure of the system because the throttling exists even if the working pressure of the bucket linkage V7 is smaller than that of the boom linkage.

Referring to fig. 12, fig. 12 is a schematic diagram illustrating the operation of the boom and arm combined operation. As shown in fig. 12, when the arm second linkage V6, the boom second linkage V4, and the boom first linkage V8 operate simultaneously, the front pump hydraulic oil flows into the boom cylinder G3 after passing through the first oil inlet P1 to the boom second linkage V4, the rear pump hydraulic oil flows into the boom cylinder G3 after passing through the second oil inlet P2 to the boom first linkage V8, and the rear pump hydraulic oil further flows into the arm second linkage V6 and then flows into the arm cylinder G4 connected to the arm second linkage V6.

Referring to fig. 13 again, fig. 13 is a schematic diagram of boom regeneration operation. As shown in fig. 13, the boom regeneration function is to regenerate the hydraulic oil of the boom cylinder large chamber G31 to the boom cylinder small chamber G32 during the boom-down process, to prevent suction, and to achieve the boom-down controllability. The specific working process is as follows: the valve core of the first boom linkage V8 works at the right position, hydraulic oil entering through the second oil inlet P2 enters the small boom cylinder cavity G32 through the first boom linkage V8, oil returning from the large boom cylinder cavity G31 passes through the valve core of the first boom linkage V8, and due to the fact that the oil returning area is small, the pressure of the large boom cylinder cavity G31 is higher than that of the small boom cylinder cavity G32. Part of the hydraulic oil in the boom cylinder large chamber G31 passes through the internal oil passage of the spool of the boom first joint V8 and enters the boom cylinder small chamber G32, thereby realizing the regeneration function.

It is worth noting that the utility model discloses a multichannel control valve still can realize the dipper regeneration function, and its theory of operation is the same with swing arm regeneration function, just has no longer been described herein.

Referring to fig. 14 again, fig. 14 is a working principle diagram of bucket confluence. As shown in fig. 14, the bucket confluence function means that, during the bucket recovery process, oil is supplied by using two pumps, thereby increasing the bucket recovery speed, preventing the suction phenomenon during the bucket recovery process, and enhancing the controllability of the bucket. The specific working process is as follows: when the bucket linkage V7 works, a valve core of the bucket linkage V7 is reversed, meanwhile, pilot oil (namely front pump hydraulic oil entering through a first oil inlet P1) collected by the bucket controls a bypass valve V11 to work at a left position, and at the moment, the front pump hydraulic oil entering through the first oil inlet P1 enters a small cavity G11 of a bucket oil cylinder G1 together with rear pump hydraulic oil entering through a second oil inlet P2 through an internal oil passage to realize confluence.

It is worth noting that the utility model discloses a reserve joint flow function still can be realized to the multichannel control valve, and its theory of operation is the same with the scraper bowl confluence, just has not been repeated here again.

Referring to fig. 15 again, fig. 14 is a working principle diagram of the pressurization of the main relief valve. As shown in fig. 15, the main relief valve pressurization includes a digging pressurization function and a traveling pressurization function.

The excavation pressurization function is as follows: by controlling the electromagnetic valve, pilot oil enters a Pc port of the main overflow valve F2, the set pressure of the main overflow valve F2 is instantly increased, and the force of the excavator is increased;

a walking pressurization function: if any walking linkage action is provided, pilot pressure is generated at the Py port of the main overflow valve F2 through a logical relation, the pilot pressure is input into the Pc port of the main overflow valve F2, the set pressure of the main overflow valve F2 is instantly increased, and the walking traction force is improved.

According to the above-mentioned embodiment of the present invention, the following advantages are provided. Through 3-piece structural layout, the layout of the multi-way control valve is more reasonable, all oil return is integrated on the middle second valve body T2, so that the layout of oil pipes is facilitated, the oil return capacity of the multi-way control valve is increased, oil supplementing ports Rs1 and Rs2 of a double-rotary motor specially designed for a large excavator are respectively connected to the oil supplementing ports of the rotary motor, when rotary braking is carried out, oil supplementing to a low-pressure port of the motor is realized, and the motor is prevented from being emptied; the double oil return ports R1 and R2 can be connected to a hydraulic oil tank of the excavator through pipelines at the same time, oil return is achieved, and oil return back pressure is effectively reduced.

Although the present invention has been described with reference to the above embodiments, it should be understood that various changes and modifications can be made therein by those skilled in the art without departing from the spirit and the scope of the invention as defined by the appended claims.

Claims

1. A multiplex control valve, comprising: the multi-way control valve sequentially communicates with a first valve body, a second valve body and a third valve body, the second valve body comprises two oil return ports, the two oil return ports are communicated with an oil tank, the first valve body and the third valve body, and when the multi-way control valve works, return oil of the first valve body and the third valve body flows back to the oil tank through the oil return ports.

2. The multiplex control valve as defined in claim 1, wherein said first valve body comprises a left travel link (V5), a boom second link (V4), a swing link (V3), a backup link (V2), and an arm first link (V1) which are connected in sequence, and said third valve body comprises a straight travel link (V10), a right travel link (V9), a boom first link (V8), a bucket link (V7), and an arm second link (V6) which are connected in sequence.

3. The multiplex control valve of claim 1, wherein said second valve body comprises an arm regeneration valve (V13), a boom back pressure valve (V12).

4. The multiplex control valve of claim 2, wherein said first and third valve bodies further comprise bypass valves (V11, V14), respectively, both of said bypass valves communicating said arm second link (V6) and said arm first link (V1).

5. The multiplexed control valve of claim 2, wherein the second valve body further comprises two rotary oil replenishment ports (Rs1, Rs2) that communicate with a dual rotary motor.

6. The multiplex control valve of claim 2, said first valve body including a first oil inlet (P1) and said second valve body including a second oil inlet (P2).

7. The multiple control valve according to claim 6, characterized in that front pump hydraulic oil is passed through a first oil inlet (P1) to the left running gear (V5) and/or rear pump hydraulic oil is passed through a second oil inlet (P2) to the right running gear (V9).

8. A multiple control valve according to claim 6, characterized in that the front pump hydraulic oil is led to the swivel joint (V3) via a first oil inlet (P1).

9. A multiple control valve according to claim 6, characterized in that the front pump hydraulic oil is led via a first oil inlet (P1) to the backup connection (V2).

10. The multiple control valve of claim 6, wherein the rear pump hydraulic oil is routed to the bucket hitch (V7) through a second oil inlet (P2).

11. The multiple control valve of claim 6, wherein front pump hydraulic oil flows through the first oil inlet (P1) to the first arm (V1), rear pump hydraulic oil flows through the second oil inlet (P2) to the second arm (V6), and when the valves are combined internally, the rear pump hydraulic oil flows into the bucket cylinder together with the front pump hydraulic oil after passing through the second valve body and the first valve body in sequence.

12. The multiplex control valve of claim 6, wherein front pump hydraulic oil is supplied to said arm first link (V1) through said first oil inlet (P1), and rear pump hydraulic oil is supplied to said arm second link (V6) through said second oil inlet (P2), said multiplex control valve further comprising an external conduit communicating said arm second link (V6) with said bucket cylinder, said rear pump hydraulic oil flowing into said bucket cylinder through said external conduit when the valves merge externally.

13. The multiple control valve according to claim 6, wherein a front pump hydraulic oil is supplied to the second boom linkage (V4) through the first oil inlet (P1), a rear pump hydraulic oil is supplied to the first boom linkage (V8) through the second oil inlet (P2), and when the front pump hydraulic oil and the rear pump hydraulic oil are merged in the valve, the front pump hydraulic oil sequentially passes through the second valve body and the third valve body and then flows into a boom cylinder together with the rear pump hydraulic oil.

14. The multiple control valve according to claim 13, wherein when the bucket link (V7), the second boom link (V4) and the first boom link (V8) operate simultaneously, the front pump hydraulic oil flows into the boom cylinder through the first oil inlet (P1) to the second boom link (V4), and the rear pump hydraulic oil flows into the boom cylinder through the second oil inlet (P2) to the first boom link (V8).

15. The multiplex control valve as defined in claim 7, wherein when said arm second link (V6), said boom second link (V4) and said boom first link (V8) are operated simultaneously, a front pump hydraulic oil is fed to said boom second link (V4) through said first oil inlet port (P1), and a rear pump hydraulic oil is fed to said boom first link (V8) through said second oil inlet port (P2).