CN213392919U - Double-loop hydraulic system with rear confluence of main throttling port - Google Patents
Double-loop hydraulic system with rear confluence of main throttling port Download PDFInfo
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- CN213392919U CN213392919U CN202022118781.8U CN202022118781U CN213392919U CN 213392919 U CN213392919 U CN 213392919U CN 202022118781 U CN202022118781 U CN 202022118781U CN 213392919 U CN213392919 U CN 213392919U
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Abstract
A double-circuit hydraulic system with rear confluence of main throttling ports. The problems of complex structure and difficult confluence of a medium-double pump or multi-pump hydraulic system are solved. The oil inlet of the first main oil inlet is connected with the oil inlet of the first main reversing valve, the second main oil inlet is connected with the oil inlet of the first auxiliary reversing valve, and the oil outlet of the first main reversing valve and the oil outlet of the first auxiliary reversing valve are connected with the first working oil port after passing through the first main reversing valve. The beneficial effects of the utility model are that, through the mode in two return circuits, realize hydraulic system's rational distribution, to compound action promoting to some extent promptly and look after the energy consumption simultaneously and generate heat.
Description
Technical Field
The utility model relates to a hydraulic system, concretely relates to double circuit hydraulic system of confluence behind main throttle mouth.
Background
The hydraulic system is generally divided into a single pump system and a multi-pump system, the single pump system realizes all actions by only one working oil pump, and the multi-pump system realizes all actions by two or more oil pumps. The single-pump system has the advantages of low cost, simple and reliable system, but is difficult to realize simultaneous work of a plurality of actions, and even the plurality of actions can be realized by the forced throttling of the low-pressure side, the single-pump system has the defects of high pressure loss and large heat productivity; the double-pump or multi-pump system has the advantages of being capable of well realizing multi-action simultaneous movement and relatively low in energy consumption, but has the problems of complex system and high cost.
The common single pump system comprises a series/parallel loop of an open center system, a compensation system before a valve of a closed center, a compensation system after the valve and the like; the double-pump and multi-pump systems are commonly used for excavating machinery and are provided with a double-loop hydraulic system with complex logic relation and the like. The confluence of the existing double-pump and multi-pump hydraulic systems is usually realized through a confluence valve, the control logic on the whole is complex, the pipeline arrangement is complex and huge, and the confluence is unreliable, and the action of low pressure needs to be forced to be boosted to be combined with high pressure by compensation during the combined action to realize the combined action, so that extra additional pressure loss and heat generation are brought in the compensation link, and the energy consumption is high.
SUMMERY OF THE UTILITY MODEL
For solving among the background art double pump or many pump hydraulic system structure complicacies, the problem of confluence difficulty, the utility model provides a double-circuit hydraulic system of confluence behind the main throttle mouth.
The technical scheme of the utility model is that: a double-loop hydraulic system with rear confluence of main throttle ports comprises a first main oil inlet, a second main oil inlet, a first working group and a second working group, wherein the first working group comprises at least one first working link, the first working link comprises a first working oil port, a first main reversing valve and a first auxiliary reversing valve, the second working group comprises at least one second working link, the second working link comprises a second working oil port, a second main reversing valve and a second auxiliary reversing valve, the first main oil inlet is connected with an oil inlet of the first main reversing valve, the second main oil inlet is connected with an oil inlet of the first auxiliary reversing valve, an oil outlet of the first main reversing valve and an oil outlet of the first auxiliary reversing valve are connected with the first working oil port after passing through the first main reversing valve, and the second main oil inlet is connected with an oil inlet of the second main reversing valve, the first main oil inlet is connected with an oil inlet of the second auxiliary reversing valve, and an oil outlet of the second main reversing valve and an oil outlet of the second auxiliary reversing valve are connected with an oil inlet of the second working oil port after passing through the second main reversing valve.
As an improvement of the utility model, first work ally oneself with and be equipped with first compensator, first main oil inlet link to each other through the oil inlet of first compensator and first main directional control valve, first compensator include first control chamber and first spring chamber, the pressure oil of first main directional control valve oil outlet department links to each other with first spring chamber, first feedback oil circuit, the opening of the pressure oil of first compensator exit and the elastic force in spring chamber, the pressure oil of first main directional control valve oil outlet department of selecting in first control chamber mutually supported control first compensator.
As a further improvement, the first main reversing valve on be equipped with first main choke, the pressure oil of first main choke oil outlet department all links to each other with first feedback oil circuit through first check valve in different first work antithetical couplet on the first working group.
As a further improvement of the present invention, the pilot oil circuit is further provided with a pilot oil circuit for driving the first main directional control valve and the second main directional control valve to operate, the pilot oil circuit is connected to the control chamber of the first main directional control valve through the first pilot control valve, the pilot oil circuit is connected to the control chamber of the second main directional control valve through the second pilot control valve, the first pilot control valve and the second pilot control valve respectively have the first position when being installed and the second position for opening the pilot oil to operate through the first main directional control valve and the second main directional control valve respectively.
As a further improvement, the first supplementary switching-over valve have the primary importance when installation and open the secondary importance that the second owner oil inlet of being convenient for links to each other with first working fluid port, first supplementary switching-over valve be automatically controlled switching-over valve.
As the utility model discloses a further improvement still includes the first guide's oil circuit that is used for driving first main directional control valve action, first main directional control valve on be equipped with first guide's break-make return circuit, second main directional control valve on be equipped with second guide's break-make return circuit, first guide's oil circuit pass through second guide's break-make return circuit on the second main directional control valve and should ally oneself with first supplementary switching-over valve control chamber on link to each other.
As a further improvement, the system further comprises a second pilot oil path for driving the second main directional control valve to act, the second pilot oil path is connected with a second auxiliary directional control valve control cavity on the first main directional control valve through a first pilot on-off loop, and the first pilot oil path and the second pilot oil path are both provided with shuttle valves.
As the utility model discloses a further improvement, first guide's break-make return circuit and second guide's break-make return circuit are realized first guide's oil circuit, second guide's oil circuit break-make function by the valve rod of the first main change valve of its place antithetical couplet, the valve rod drive switching-over of second main change valve respectively.
As a further improvement, the pilot operated directional control valve of first supplementary switching-over valve for having the on-off formula or for the valve rod is the pilot operated proportional control valve of proportional formula, first supplementary switching-over valve for the pilot operated directional control valve and by this first guide's oil circuit drive of antithetical couplet its action.
As a further improvement of the utility model, the first auxiliary reversing valve is provided with an auxiliary throttle orifice and/or a load one-way valve.
The beneficial effects of the utility model are that, through the mode in two return circuits, realize hydraulic system's rational distribution, to compound action promoting to some extent promptly and look after the energy consumption simultaneously and generate heat. The utility model discloses simple structure still has, convenient assembling, and the action is reliable, advantages such as long service life.
Drawings
Fig. 1 is a hydraulic principle schematic diagram of a first embodiment of the present invention.
Fig. 2 is a schematic view of a hydraulic principle of the second embodiment of the present invention.
Fig. 3 is an enlarged schematic view of the first main directional control valve 32 of fig. 1.
Fig. 4 is an enlarged schematic view of the first auxiliary direction valve 33 of fig. 1.
Fig. 5 is a schematic view of the first auxiliary direction valve 33 of fig. 2.
Fig. 6 is an enlarged schematic view of the first main directional control valve 32 of fig. 2.
Fig. 7 is an enlarged schematic view of the first main directional control valve 32 of fig. 6.
In the figure, 1, a first working group; 2. a second workgroup; 3. a first working unit; 31. a first working oil port; 32. a first main directional control valve; 33. a first auxiliary directional control valve; 331. an auxiliary choke; 332. a load check valve; 34. a first primary orifice; 35. a first pilot on-off loop; 36. a second pilot on-off loop; 4. a second working unit; 41. a second working oil port; 42. a second main directional control valve; 43. a second auxiliary directional control valve; 5. a first compensator; 6. a first check valve; 7. a pilot oil path; 71. a first pilot control valve; 72. a second pilot control valve; 73. a first pilot oil passage; 74. a second pilot oil passage; 8. a shuttle valve; p1, a first main oil inlet; p2, a second main oil inlet; LS1, first feedback oil path.
Detailed Description
The embodiments of the present invention will be further explained with reference to the accompanying drawings:
referring to fig. 1 and fig. 2-7, a dual-circuit hydraulic system with main throttles converging behind includes a first main oil inlet P1, a second main oil inlet P2, a first working group 1 and a second working group 2, where the first working group includes at least one first working link 3, the first working link includes a first working oil port 31, a first main directional control valve 32 and a first auxiliary directional control valve 33, the second working group includes at least one second working link 4, the second working link includes a second working oil port 41, a second main directional control valve 42 and a second auxiliary directional control valve 43, the first main oil inlet is connected to an oil inlet of the first main directional control valve, the second main oil inlet is connected to an oil inlet of the first auxiliary directional control valve, an oil outlet of the first main directional control valve and an oil outlet of the first auxiliary directional control valve are both connected to the first working oil port after passing through the first main directional control valve, the second main oil inlet is connected with an oil inlet of a second main reversing valve, the first main oil inlet is connected with an oil inlet of a second auxiliary reversing valve, and an oil outlet of the second main reversing valve and an oil outlet of the second auxiliary reversing valve are connected with an oil inlet of a second working oil port after passing through the second main reversing valve. The beneficial effects of the utility model are that, through the mode in two return circuits, realize hydraulic system's rational distribution, to compound action promoting to some extent promptly and look after the energy consumption simultaneously and generate heat. The utility model discloses simple structure still has, convenient assembling, and the action is reliable, advantages such as long service life. During specific composite action, the flow is converged behind the main throttling port and compensated in front of the main throttling port, so that the energy consumption is low and the environment is protected. In particular, the second working pair and the first working pair may be similar or identical. More specifically speaking, the utility model discloses a P1 is first workgroup fuel feeding, and P2 realizes the two return circuits fuel feeding of double pump for the fuel feeding of second workgroup. When the composite action is carried out, the auxiliary reversing valve is adjusted, so that the second main oil inlet can supply oil for the first working oil port, the first main oil inlet can supply oil for the second working oil port, the reliable confluence is realized, and the control of the composite action is reliable. Through the setting of first main switching-over valve, second main switching-over valve, first supplementary switching-over valve and second supplementary switching-over valve, realize quick reliable confluence, and the energy consumption is low.
The first working group comprises two, three or four first working couples. Specifically, the second working group comprises one, two, three or four second working groups. The structure enables the system to supply oil to two to eight working devices (the working devices are actuating elements, and working oil ports such as A1A2A3A4 … … are formed in a schematic diagram), and the working devices can supply oil to the working devices by one pump or two pumps. This patent describes a typical four-operation device (i.e., A1A2A3a4 four working ports for output, which are used to drive four actuators, such as cylinders and motors). When one of the pumps supplies oil to the pump, the oil supply can be realized only by the action of the main reversing valve; when the other pump supplies oil to the other pump, the other pump needs to be supplied with oil through the auxiliary reversing valve. Two of the four-linkage working mechanism are arranged on the same side, the P1 supplies oil to the A1B1/A2B2 working device through the first main reversing valve of A1B1/A2B2, and supplies oil to the A3B3/A4B4 through the second auxiliary reversing valve, at the moment, the valve rod of the first main reversing valve is provided with a first main throttling port 34, and the second auxiliary reversing valve is provided with an auxiliary throttling port 331 serving as an auxiliary throttling port. The P2 oil supply is a duplicate of the P1 oil supply. A1B1/A2B2 is arranged on one side, and A3B3/A4B4 is arranged on the other side, which is for the sake of simplicity of principle, and of course, the A1B1/A2B2/A3B3/A4B4 may be arranged crosswise. The utility model discloses in, when P1 and P2 combined action just for A1B1 fuel feeding, it is the A1B1 fuel feeding behind the first main change valve again after the oil-out department confluence of first main change valve (confluence behind the first main throttle mouth), can cancel the loss of pressure through pressure compensator department completely, further reduce energy consumption and calorific capacity.
The first working connection is provided with a first compensator 5, a first main oil inlet is connected with an oil inlet of a first main reversing valve through the first compensator, the first compensator comprises a first control cavity and a first spring cavity, pressure oil at an oil outlet of the first main reversing valve is connected with the first spring cavity and a first feedback oil path, and the first control cavity selects the pressure oil at an outlet of the first compensator, the elastic force of the spring cavity and the pressure oil at an oil outlet of the first main reversing valve to be matched with each other to control the opening of the first compensator. Specifically, the first main reversing valve is provided with a first main throttling port 34, and pressure oil at an oil outlet of the first main throttling port of different first working links on the first working group is connected with a first feedback oil path LS1 through a first one-way valve 6. The utility model discloses the first compensator that is used for compensation before the valve has been increased. The function of the pre-valve compensation is to keep the pressure difference before and after the main throttling port unchanged, when the pre-valve compensation is operated alone, the flow output by the main throttling port is only related to the opening size determined by the stroke of the valve rod and is not related to the size of the load, and when the pre-valve compensation is operated in a compound mode, the flow of the small load is preferentially supplied. LS is a spring cavity acting on the compensator in front of the valve, and the pressure difference between the front and the rear of the main throttling port is maintained to be positively correlated with the spring of the compensator in front of the valve by utilizing the force balance of the compensator in front of the valve. The function of adding the variable throttling device (the first compensator) in front of the valve is to improve the speed regulation controllability of the main throttling port and to improve the composite action harmony of the oil supply state of the left duplex or right duplex single pump under the flow unsaturated state (the flow required by the two actions exceeds the flow provided by the oil pump, namely the flow unsaturated state). More specifically, when the composite action is carried out, for example, the composite action of the working oil port of A1B1/A2B2, the first auxiliary reversing valve of the working oil port of A2B2 can be opened, so that the P1 supplies oil for A1 and the P2 supplies oil for A2, the boosting of a small load is not needed, and the energy consumption and the heating are avoided. The function of the check valve is to ensure that the highest pressure of each action pair can be picked up, for example, when A1 and A2 act simultaneously, the pressure of A1 is higher than that of A2, if the check valve is not arranged, the A1 sends oil to A2 through the LS oil way, the pressure of LS1 cannot reflect the highest pressure of the system, the establishment of the highest pressure of the system is influenced, and the action of A1 is further influenced. The compensator can better realize the composite action of the left duplex or the right duplex, so that the same pump drives two actions and has better composite action harmony. The compensation device in front of the valve can realize better speed regulation performance of single action, and particularly keeps the consistency of the pressure difference between the front and the rear of the main throttling port. When the pre-valve compensation device works together for A1/B1 and A2/B2 (namely two actions of oil supply of one oil pump), better composite action coordination can be provided when the flow rate provided by the oil pump exceeds the flow rate required by the two actions.
The first embodiment is as follows: the utility model discloses still including the pilot oil circuit 7 that is used for driving first main change valve, the action of second main change valve, pilot oil lu-tung link to each other through the control chamber of first pilot control valve 71 with first main change valve, pilot oil lu-tung link to each other through the control chamber of second pilot control valve 72 with the second main change valve, first pilot control valve, second pilot control valve first position when having the installation respectively with open the second position that is convenient for pilot oil through being used for driving first main change valve, the action of second main change valve respectively. Specifically, the first auxiliary reversing valve is provided with a first position when the first auxiliary reversing valve is installed and a second position where a second main oil inlet is convenient to connect with the first working oil port when the first auxiliary reversing valve is opened, and the first auxiliary reversing valve is an electronic control reversing valve. Specific theory, the utility model discloses can realize the switching-over of first main switching-over valve, second main switching-over valve, first supplementary switching-over valve and the supplementary switching-over valve of second through automatically controlled mode. For the electric control scheme, electric control is flexible, changeable and controllable, and can be controlled according to human thought, so that the electric control scheme is simple.
Example two: the utility model discloses still including the first guide's oil circuit 73 that is used for driving first main directional control valve action, first main directional control valve on be equipped with first guide break-make return circuit 35, second main directional control valve on be equipped with second guide break-make return circuit 36, first guide oil sweetgum fruit on through second main directional control valve on the second guide break-make return circuit and should ally oneself with first supplementary switching-over valve control chamber on link to each other. Specifically, the pilot oil circuit comprises a second pilot oil circuit 74 used for driving a second main reversing valve to act, the second pilot oil circuit is connected with a second auxiliary reversing valve control cavity on the second main reversing valve through a first pilot on-off circuit on the first main reversing valve, and the first pilot oil circuit and the second pilot oil circuit are both provided with shuttle valves 8. More specifically, the first pilot on-off loop and the second pilot on-off loop are driven by a valve rod of a first main reversing valve and a valve rod of a second main reversing valve of the first pilot on-off loop and the second pilot on-off loop respectively to be reversed so as to realize the on-off function of the first pilot oil path and the second pilot oil path. More specifically, the first auxiliary reversing valve is a hydraulic control reversing valve with an on-off type or a hydraulic control proportional regulating valve with a proportional type valve rod, and the first auxiliary reversing valve is a hydraulic control reversing valve and is driven to act by the first pilot oil path. More specifically, the first auxiliary reversing valve is provided with an auxiliary throttle 331 and/or a load check valve 332. The arrangement of the first check valve and the load check valve enables the system to pick up the highest pressure for feedback during compound action, and the situation that when one working device is high in pressure and one working device is low in pressure, the flow of the high-pressure side reversely enters the low-pressure side is avoided. The utility model discloses a set up first guide break-make return circuit, second guide break-make return circuit at the both ends of first main change valve, second main change valve, and realize its break-make by the main valve stem drive of this first main change valve, second main change valve that allies oneself with to when making the compound action, make an oil pump correspond an action, no longer produce the contact between another action, be independent mutually. When the connection does not act, the pilot oil of the first pilot oil path can pass through, and when the connection does any action, the pilot oil path can be cut off. For example, referring to fig. 2, 5, 6, and 7, a pilot oil is led out from a shuttle valve through a valve a1 and B1, passes through a second pilot on-off oil passage of the A3/B3 working link, is connected in series through a second pilot on-off circuit of the a4/B4 working link, and reaches a first auxiliary directional control valve control chamber of the a1/B1 working link.
When only A1/B1 works, the pilot oil of a1 and B1 controls the first main reversing valve to reverse, the oil of P1 can pass through, and the other part of the pilot oil of a1 and B1 passes through the shuttle valve and then reaches the first auxiliary reversing valve control cavity of the working connection of A1/B1 through the second pilot on-off circuit of the connection of A3/B3 and the connection of A4/B4, so that the oil of the P2 oil pump can supply oil to A1/B1.
When A1/B1 and A3/B3 or A4/B4 work together, at the moment, the second pilot oil on-off circuit is reversed along with the reversing of any one of A3/B3 and A4/B4, the oil circuit of the first auxiliary reversing valve, which controls A1/B1, of a1 and B1 is cut off, the valve rod of the first auxiliary reversing valve is reset under the action of a spring cavity spring, the circuit of the P2 oil pump supplying oil to A1/B1 is cut off, and the composite action independence under the hydraulic control is achieved. Namely, the P1 is the combined oil supply of A1/B1, and the P2 is the oil supply of A3/B3 or A4/B4.
The utility model discloses a pilot oil in each work antithetical couplet picks up the back through the shuttle valve in the liquid accuse scheme, and the pilot break-make oil return of the main oil supply work antithetical couplet of another oil pump again, if there is such pilot break-make return circuit of multichannel, then need establish ties to it, controls the auxiliary control choke of this work antithetical couplet, realizes logical: when one working unit works independently, the double pumps can be combined; when the main oil supply work of the two oil pumps or the oil pumps are connected to work together, the two oil pumps respectively supply oil for the corresponding working mechanism. The first auxiliary reversing valve and the second auxiliary reversing valve are on-off hydraulic control reversing valves or proportional hydraulic control proportional regulating valves with proportional valve rods. The first auxiliary reversing valve and the second auxiliary reversing valve can be made into a switch type or a proportional relation with the pilot oil. The proportional auxiliary reversing valve enables the product to be adjusted more accurately and saves more energy. The utility model provides a first main change valve, second main change valve realize for the tribit eight leads to the switching-over valve, and the proportional reversing valve that also can adopt the oil control of leading of course realizes, makes equipment have reciprocating work's function.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplification of the description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art. In addition, in the description of the present invention, "a plurality" means two or more unless otherwise specified.
The skilled person should understand that: although the present invention has been described in accordance with the above embodiments, the inventive concept is not limited to this embodiment, and any modification of the inventive concept will be included in the scope of the patent claims.
Claims (10)
1. A double-loop hydraulic system with rear confluence of main throttling ports is characterized by comprising a first main oil inlet (P1), a second main oil inlet (P2), a first working group (1) and a second working group (2), wherein the first working group comprises at least one first working link (3), the first working link comprises a first working oil port (31), a first main reversing valve (32) and a first auxiliary reversing valve (33), the second working group comprises at least one second working link (4), the second working link comprises a second working oil port (41), a second main reversing valve (42) and a second auxiliary reversing valve (43), the first main oil inlet is connected with the oil inlet of the first main reversing valve, the second main oil inlet is connected with the oil inlet of the first auxiliary reversing valve, the oil outlet of the first main reversing valve and the oil outlet of the first auxiliary reversing valve are connected with the first working oil port after passing through the first main reversing valve, the second main oil inlet is connected with an oil inlet of a second main reversing valve, the first main oil inlet is connected with an oil inlet of a second auxiliary reversing valve, and an oil outlet of the second main reversing valve and an oil outlet of the second auxiliary reversing valve are connected with an oil inlet of a second working oil port after passing through the second main reversing valve.
2. The double-circuit hydraulic system with the rear confluence of the main throttling ports as claimed in claim 1, wherein the first working connection is provided with a first compensator (5), the first main oil inlet is connected with the oil inlet of the first main directional control valve through the first compensator, the first compensator comprises a first control cavity and a first spring cavity, pressure oil at the oil outlet of the first main directional control valve is connected with the first spring cavity and the first feedback oil path, and the first control cavity selects the pressure oil at the outlet of the first compensator to be matched with the elastic force of the spring cavity and the pressure oil at the oil outlet of the first main directional control valve to control the opening of the first compensator.
3. The dual-circuit hydraulic system with rear confluence of main throttling ports as claimed in claim 1, wherein the first main directional control valve is provided with a first main throttling port (34), and the pressure oil at the oil outlet of the first main throttling port of different first working links of the first working group is connected with the first feedback oil path (LS 1) through a first one-way valve (6).
4. The dual-circuit hydraulic system with rear confluence of main throttling ports as claimed in claim 1, further comprising a pilot oil path (7) for actuating the first and second main directional control valves, wherein the pilot oil path is connected to the control chamber of the first main directional control valve through a first pilot control valve (71), and the pilot oil path is connected to the control chamber of the second main directional control valve through a second pilot control valve (72), and the first and second pilot control valves respectively have a first position when installed and a second position when opened to facilitate the actuation of the pilot oil through the first and second main directional control valves respectively.
5. The dual circuit hydraulic system of claim 4, wherein the first auxiliary direction valve has a first position when installed and a second position when opened to facilitate connection of the second main oil inlet with the first working oil port, the first auxiliary direction valve being an electronically controlled direction valve.
6. The double-circuit hydraulic system with rear confluence of main throttling ports as claimed in claim 1, further comprising a first pilot oil circuit (73) for driving the first main directional control valve to act, wherein the first main directional control valve is provided with a first pilot on-off circuit (35), the second main directional control valve is provided with a second pilot on-off circuit (36), and the first pilot oil circuit is connected with the first auxiliary directional control valve control chamber of the double-circuit hydraulic system through the second pilot on-off circuit of the second main directional control valve.
7. The dual-circuit hydraulic system with rear confluence of main throttling ports as claimed in claim 6, further comprising a second pilot oil path (74) for driving a second main directional control valve to act, wherein the second pilot oil path is connected with a second auxiliary directional control chamber on the second main directional control valve through a first pilot on-off circuit on the first main directional control valve, and the first pilot oil path and the second pilot oil path are both provided with a shuttle valve (8).
8. The dual-circuit hydraulic system with rear confluence of main throttling ports as claimed in claim 7, wherein the first pilot on-off circuit and the second pilot on-off circuit are driven by the valve rod of the first main reversing valve and the valve rod of the second main reversing valve respectively to realize the on-off function of the first pilot oil path and the second pilot oil path.
9. The dual-circuit hydraulic system with rear confluence of main chokes as claimed in claim 6, wherein the first auxiliary directional control valve is a pilot operated directional control valve with on-off type or a pilot operated proportional control valve with proportional type valve stem, and the first auxiliary directional control valve is a pilot operated directional control valve and is driven by the first pilot oil path.
10. A dual circuit hydraulic system with merging rear main chokes according to claim 5 or 9, characterized in that the first auxiliary directional control valve is provided with an auxiliary choke (331) and/or a load check valve (332).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022118781.8U CN213392919U (en) | 2020-09-24 | 2020-09-24 | Double-loop hydraulic system with rear confluence of main throttling port |
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| CN202022118781.8U CN213392919U (en) | 2020-09-24 | 2020-09-24 | Double-loop hydraulic system with rear confluence of main throttling port |
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| CN213392919U true CN213392919U (en) | 2021-06-08 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112112849A (en) * | 2020-09-24 | 2020-12-22 | 圣邦集团有限公司 | Double-loop hydraulic system with rear confluence of main throttling port |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112112849A (en) * | 2020-09-24 | 2020-12-22 | 圣邦集团有限公司 | Double-loop hydraulic system with rear confluence of main throttling port |
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