CN218235646U - Proportional combination valve structure suitable for rotary drilling rig - Google Patents
Proportional combination valve structure suitable for rotary drilling rig Download PDFInfo
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- CN218235646U CN218235646U CN202222472189.7U CN202222472189U CN218235646U CN 218235646 U CN218235646 U CN 218235646U CN 202222472189 U CN202222472189 U CN 202222472189U CN 218235646 U CN218235646 U CN 218235646U
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Abstract
The utility model relates to the technical field of proportional valves, in particular to a proportional combination valve structure suitable for a rotary drilling rig, which comprises a valve main body, a hydraulic oil supply source and an oil return tank, wherein a first action control valve group of the valve main body comprises a main winch control assembly and a power head rotation control assembly; the second action control valve group of the valve main body comprises an auxiliary hoisting control assembly, a variable amplitude control assembly, a left walking control assembly and a right walking control assembly; the third action control valve group of the valve main body comprises a rotary positioning control assembly, a pressurization control assembly, a track widening control assembly and a mast control assembly; any control assembly comprises an electro-hydraulic proportional valve, and two working oil ports of the valve are respectively connected with an oil inlet and an oil return port of a load; the oil inlet and the oil return port of the valve are respectively connected with the oil inlet and the oil return pipeline of the action control valve group. The utility model provides high control accuracy and more energy-conserving supports each action joint of rig and realizes compound action, has practiced thrift the action time, has improved action efficiency.
Description
Technical Field
The utility model relates to a proportional valve technical field, concretely relates to proportional combined valve structure suitable for dig rig soon.
Background
When the rotary drilling rig works, the operation of the equipment is realized by controlling hydraulic oil to each action mechanism (a hydraulic pump or a hydraulic cylinder) of the drilling rig, and the equipment comprises the steps of whole machine walking, crawler widening, rotary positioning of a chassis upper structure, hoisting of a drill rod, stable structure during drilling and digging, rotation of a drill bit, mast action of cantilever swinging, amplitude variation of a cantilever supporting structure and the like. Generally, a plate type multi-way valve scheme is adopted to realize oil circuit control of different actions and corresponding action control. For example, the control of the mast movements during boom swing requires a corresponding number of valves, while the control of the luffing during boom support is controlled via further valves.
Because the sheet type multi-way valve scheme is adopted to realize the control of each action, a series of actions of the drilling machine are in a single-step sequential structure under common conditions, for example, the cantilever cannot perform the main hoisting action of a drill rod when swinging, or the cantilever cannot perform the amplitude variation action of a support structure to keep the balance among the structures when lifting and swinging. However, in actual conditions, in order to avoid the obstruction of some motion spaces and save motion time and energy consumption, several motion joints need to act simultaneously, that is, the equipment needs to be capable of performing a series of compound motions. For example, the drill pipe needs to be lifted (main hoisting) while the boom is lifted. In the conventional chip valve group control, the effect of the cooperative motion of the motion joints cannot be flexibly realized due to the adoption of a single-step sequential control mode. Therefore, when the equipment works, more operation time is consumed, the working efficiency is influenced, and the avoidance paths of all structures also need to be planned in advance, so that the paths are planned again and frequently adjusted after the equipment easily encounters obstacles in the action process. Although in some large-flow control scenes, the compound action can be realized through the two-piece type valve, the structure is obviously bulkier, the installation and maintenance are influenced, and the unstable operation factors caused by the complicated structure are increased.
In summary, the conventional plate valve set has the following disadvantages:
1) The valve core has low flow control resolution and large flow gradient, and cannot realize soft and accurate action control: that is, the traditional plate valve scheme cannot give consideration to the matching of a large flow valve and a small flow valve, and is limited by specifications, and a large flow actuating mechanism can be realized only by two confluence; the small-flow executing mechanism is realized by limiting the stroke of the valve core, so that the pipeline connection of the control valve of the large-flow executing mechanism is complicated, the control flow resolution is low, the flow gradient of the small-flow valve is consistent with the flow gradient of the corresponding large-flow valve, and the flexible control cannot be realized;
2) The pressure drop of the configured pressure compensator is large, so that large reactive power loss of each actuating mechanism is caused;
3) The oil source needs to be controlled in a pilot mode to enter a cab of the drilling machine, and the control pipeline is complex in connection;
4) The structure is overall heavy and integrated, the installation and maintenance difficulty is increased, and for example, when a certain valve is maintained, the valve is integrally disassembled and assembled.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a proportional combined valve structure suitable for dig rig soon solves above technical problem.
The utility model solves the technical problem that the following technical scheme can be adopted to realize:
a proportional combined valve structure suitable for a rotary drilling rig comprises a valve main body, a hydraulic oil supply source and an oil return tank, wherein the hydraulic oil supply source is connected with the valve main body and then supplies hydraulic oil to the valve main body, each hydraulic pump (hydraulic motor) and each hydraulic cylinder (hydraulic rod) of the rotary drilling rig are connected with the valve main body, the valve main body is used for controlling each hydraulic pump and each hydraulic cylinder to realize the action control of the rotary drilling rig, an oil inlet and an oil outlet of the oil return tank are respectively connected with the valve main body and the hydraulic oil supply source, wherein,
the valve main body comprises a first action control valve group, a second action control valve group and a third action control valve group, wherein the first action control valve group comprises a main winch control assembly and a power head rotation control assembly, the main winch hydraulic pump and the power head rotation hydraulic pump of the rotary drilling rig are respectively controlled by the main winch hydraulic pump and the power head rotation hydraulic pump to realize action control of a rotary drum and a drill bit of a drill rod of the rotary drilling rig so as to perform drilling and unloading operations, the drill rod is connected to a gooseneck at the top of the rotary drilling rig, the main winch is operated to lift or lower the drill rod, the power head rotation is operated to enable the drill bit and the rotary drum to work to perform rotary drilling or unloading, the main winch control assembly is connected with the main winch hydraulic pump of the rotary drilling rig, and the power head rotation control assembly is connected with the rotation hydraulic pump of the rotary drilling rig;
the second action control valve group comprises an auxiliary hoisting control component, a variable amplitude control component, a left walking control component and a right walking control component, wherein the auxiliary hoisting hydraulic pump, the variable amplitude hydraulic cylinder, the left walking hydraulic pump and the right walking hydraulic pump of the rotary drilling rig are respectively controlled to realize the control of actions of an auxiliary hoisting (the action control is usually used for hoisting and controlling a drill rod during maintenance, the operation requirements such as hoisting time required by the operations are lower), and the variable amplitude (before drilling and digging operations are carried out, a support where the drill rod is located and a mast structure and the like are required to be adjusted to a certain angle in advance, the process is variable amplitude), left walking (left crawler walking control) and right walking (right crawler control), and the auxiliary hoisting control component, the variable amplitude control component, the left walking control component and the right walking control component are respectively connected with the auxiliary hoisting hydraulic pump, the variable amplitude hydraulic cylinder, the left walking hydraulic pump and the right walking hydraulic pump of the rotary drilling rig;
the third action control valve group comprises a rotary positioning control component, a pressurization control component, a track widening control component and a mast control component, wherein the rotary positioning hydraulic pump, the pressurization hydraulic cylinder, the track widening hydraulic cylinder and the mast hydraulic cylinder are respectively controlled to realize rotary positioning (the action enables structures such as a control carriage, a lifting rod and the like on a chassis to rotate a certain angle relative to the chassis), pressurization (a drill bit of a drill rod can deeply and downwards probe after auxiliary pressurization), track widening (the action increases the distance between a left track and a right track which are moved, so that the chassis of the whole machine is more stable, rotary drilling operation is facilitated) and action control of the mast, and the rotary positioning control component, the pressurization control component, the track widening control component and the mast control component are respectively connected with the rotary positioning hydraulic pump, the pressurization hydraulic cylinder, the track hydraulic cylinder and the mast hydraulic cylinder of the rotary drilling rig;
an oil supply port of the hydraulic oil supply source is connected with oil inlets of control assemblies of the first action control valve group, the second action control valve group and the third action control valve group so as to provide hydraulic oil for the assemblies of the valve groups;
oil return ports of the control assemblies of the first action control valve group, the second action control valve group and the third action control valve group are connected to the oil return tank, so that hydraulic oil is returned;
any one of the main winch control assembly, the power head rotation control assembly, the auxiliary winch control assembly, the amplitude variation control assembly, the left walking control assembly, the right walking control assembly, the rotation positioning control assembly, the pressurization control assembly, the track widening control assembly and the mast control assembly comprises an electro-hydraulic proportional valve, a first working oil port and a second working oil port of the electro-hydraulic proportional valve are a first working oil port and a second working oil port of the control assembly where the electro-hydraulic proportional valve is located, the first working oil port and the second working oil port of each control assembly are respectively connected with an oil inlet and an oil return port of a load (a hydraulic pump or a hydraulic cylinder) connected with the electro-hydraulic proportional valve, for example, when the control assembly is the main winch control assembly, the first working oil port and the second working oil port of the electro-hydraulic proportional valve are respectively connected with the oil inlet and the oil return port of the main winch hydraulic pump;
and an oil inlet and an oil return port of the electro-hydraulic proportional valve are respectively connected with an oil inlet pipeline and an oil return pipeline of the action control valve group where the control assembly is located.
The utility model discloses a set up three action control valves, each control assembly to digging the rig soon carries out rational planning, it is first, two, three action control valves plan the back according to the required pressure size of each subassembly, join in marriage the control assembly that pipeline flow is close and organize together, for example main hoist control and the unit head gyration that will need great hydraulic power are realized controlling by the first action control valves of relative independence, with this rational planning flow distribution, alleviate the fuel feeding load of hydraulic oil supply source, improve the pipe-line transportation efficiency, stability when also increasing the pipeline infusion.
Any one of the main winch control assembly, the power head control assembly, the left walking control assembly and the right walking control assembly further comprises a pressure compensation valve and a shuttle valve, and the pressure compensation valve is connected between an oil inlet of an electro-hydraulic proportional valve of the control assembly and an oil inlet pipeline of an action control valve group where the pressure compensation valve is located;
two oil inlets of the shuttle valve are respectively connected between a first working oil port and a second working oil port of the electro-hydraulic proportional valve;
overflow valves are arranged between the first working oil port and the oil return port of the electro-hydraulic proportional valve, between the second working oil port and the oil return port, and between the pressure compensation valve and the oil outlet of the shuttle valve.
Overflow valves are arranged between the first working oil port and the oil return port of the electro-hydraulic proportional valve of any one of the auxiliary winch control assembly and the amplitude variation control assembly, and between the second working oil port and the oil return port.
Any one of the rotary positioning control assembly, the track widening control assembly and the mast control assembly further comprises a shuttle valve, two oil inlets of the shuttle valve are respectively connected between a first working oil port and a second working oil port of the control assembly, and overflow valves are respectively arranged between the first working oil port and an oil return port, and between the second working oil port and the oil return port of an electro-hydraulic proportional valve of the control assembly;
the electro-hydraulic proportional valve is connected with an oil inlet pipeline of the action control valve group where the control assembly is located through another overflow valve, and the other overflow valve is also connected with an oil outlet of the shuttle valve.
The pressurization control component comprises a shuttle valve, two oil inlets of the shuttle valve are respectively connected with a first working oil port and a second working oil port of an electro-hydraulic proportional valve of the pressurization control component,
first overflow valves are arranged between the first working oil port and the oil return port of the electro-hydraulic proportional valve and between the second working oil port and the oil return port,
an oil inlet of the electro-hydraulic proportional valve is connected with an oil inlet pipeline of the third action control valve group through a second overflow valve,
the oil outlet of the shuttle valve is connected with the oil return port of the electro-hydraulic proportional valve through a third overflow valve, and the oil outlet of the shuttle valve is connected with the second overflow valve.
The hydraulic oil supply source comprises a variable displacement plunger pump, and the hydraulic oil is supplied to the first action control valve group, the second action control valve group and the third action control valve group through the variable displacement plunger pump.
The hydraulic oil supply source adopts a duplex variable plunger pump, and double-path oil supply is realized so as to ensure stable oil supply.
When the dual pump is adopted, the first path of the dual pump supplies oil to one end of an oil inlet pipeline of the first action control valve group and the second action control valve group, and the second path of the dual pump supplies oil to the third action control valve group and the other end of the oil inlet pipeline of the first action control valve group. At this time, the proportional pressure reducing valve is disposed between the power head rotation component and the first oil supply port of the hydraulic oil supply source, that is, in terms of the pipeline connection layout, the proportional pressure reducing valve is closer to the hydraulic oil supply source than other components of the first motion control valve group;
the first action control valve group comprises a proportional pressure reducing valve, an oil inlet and an oil return port of the proportional pressure reducing valve are respectively connected with the hydraulic oil supply source and the oil return tank, and a working oil port of the proportional pressure reducing valve is connected with a control oil outlet of the hydraulic oil supply source.
The third motion control valve block includes at least two mast control assemblies.
An electro-hydraulic proportional valve of the main winch control assembly is connected with a displacement sensor so as to monitor the opening of a valve port in real time and improve the winch precision;
the electro-hydraulic proportional valve of the rotary positioning control assembly is connected with another displacement sensor so as to monitor the opening of the valve port in real time and improve the rotary precision.
Has the advantages that: since the technical scheme is used, the utility model discloses for traditional piece formula multiple unit valve scheme, for plate valve scheme, constitute three function valves after according to flow size rational distribution through each control valve that will dig the rig soon, the cooperation plunger pump realizes digging the motion control of rig soon, it is more energy-conserving when making its control accuracy obtain improving, in addition because the cooperation of control structure makes each action joint of digging the rig soon simultaneously, perhaps carry out the motion in coordination according to certain action combination, action time has not only been practiced thrift, also can effectively avoid the barrier in the action route after the nimble action of messenger's rig cantilever, improve action efficiency.
Drawings
Fig. 1 is a first schematic structural diagram of the present invention;
FIG. 2 is a second schematic structural view of the present invention;
fig. 3 is a schematic structural diagram of a first type of control assembly according to the present invention;
fig. 4 is a schematic structural diagram of a second type of control assembly according to the present invention;
fig. 5 is a schematic structural diagram of a third type of control assembly according to the present invention;
fig. 6 is a schematic structural diagram of a fourth type of control assembly according to the present invention; .
Detailed Description
In order to make the technical means, creation features, achievement purposes and functions of the present invention easy to understand, the present invention will be further explained with reference to the specific drawings. It is noted that the terms "first," "second," "third," "fourth," and the like (if any) in the description and in the claims of the present invention are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It will be appreciated that the data so used may be interchanged under appropriate circumstances such that the embodiments described herein may be practiced otherwise than as specifically illustrated or described herein. Furthermore, the terms "comprises" or "comprising," and any variations thereof, are intended to cover non-exclusive inclusions, such that a product or apparatus that comprises a list of elements or units is not necessarily limited to those elements or units expressly listed, but may include other elements or units not expressly listed or inherent to such product or apparatus.
Referring to fig. 1, a proportional combination valve structure suitable for a rotary drilling rig comprises a valve main body, a hydraulic oil supply source 400 and an oil return tank 900, wherein the hydraulic oil supply source 400 is connected with the valve main body and then supplies hydraulic oil to the valve main body, each hydraulic pump (hydraulic motor) and each hydraulic cylinder (hydraulic rod) for work of the rotary drilling rig are connected with the valve main body, the valve main body controls each hydraulic pump and each hydraulic cylinder to realize the action control of the rotary drilling rig, and an oil inlet and an oil outlet of the oil return tank 900 are respectively connected with the valve main body and the hydraulic oil supply source 400.
As shown in fig. 1 and 2, the valve body includes a first motion control valve block 100, a second motion control valve block 200, and a third motion control valve block 300, wherein,
the first action control valve group 100 comprises a main hoisting control assembly 101 and a power head rotation control assembly 102, the main hoisting hydraulic pump 1001 and the power head rotation hydraulic pump 1002 of the rotary drilling rig are respectively controlled by the main hoisting control assembly and the power head rotation hydraulic pump 102 to realize action control of a rotary drum and a drill bit of a drill rod of the rotary drilling rig, so that drilling and discharging operations are performed, the drill rod is connected to a gooseneck of the top of the rotary drilling rig, the main hoisting action lifts or descends the drill rod, the power head rotation action enables the drill bit and the rotary drum to work for rotary drilling or discharging, the main hoisting control assembly 101 is connected with the main hoisting hydraulic pump 1001 of the rotary drilling rig, and the rotation control assembly 102 is connected with the power head rotation hydraulic pump 1002 of the rotary drilling rig;
the second motion control valve group 200 comprises an auxiliary winch control assembly 201, a variable amplitude control assembly 202, a left walking control assembly 203 and a right walking control assembly 204, wherein the auxiliary winch control assembly 201, the variable amplitude hydraulic cylinder 2002, the left walking hydraulic pump 2003 and the right walking hydraulic pump 2004 of the rotary drilling rig are respectively controlled to realize the control of auxiliary winch (the motion control is generally used for hoisting and controlling drill rods during maintenance, the operation requirements such as hoisting time required by the operation are low), variable amplitude (before drilling and digging operation, a support where the drill rods are located and a structure comprising a mast and the like are required to be adjusted to a certain angle in advance, the process is variable amplitude), left walking (left crawler walking control) and right walking (right crawler control), and the auxiliary winch control assembly 201, the variable amplitude control assembly 202, the left walking control assembly 203 and the right walking control assembly 204 are respectively connected with the auxiliary winch hydraulic pump 2001, the variable amplitude hydraulic cylinder 2002, the left walking hydraulic pump 2003 and the right walking hydraulic pump 2004 of the rotary drilling rig;
the third motion control valve set 300 comprises a slewing positioning control assembly 301, a pressurizing control assembly 302, a track widening control assembly 303 and a mast control assembly 304, wherein the slewing positioning hydraulic pump 3001, the pressurizing hydraulic cylinder 3002, the track widening hydraulic cylinder 3003 and the mast hydraulic cylinder 3004 are respectively controlled to realize slewing positioning (the motion enables structures such as a control carriage and a suspension rod on a chassis to rotate a certain angle relative to the chassis), pressurizing (a drill bit of a drill rod can be deeply and downwards detected after auxiliary pressurizing), track widening (the motion increases the distance between left and right travelling tracks to enable the chassis of the whole machine to be more stable and facilitate rotary drilling operation), and motion control of a mast, wherein the slewing positioning control assembly 301, the pressurizing control assembly 302, the track widening control assembly 303 and the mast control assembly 304 are respectively connected with the slewing positioning hydraulic pump 3001, the pressurizing hydraulic cylinder 3002, the track widening hydraulic cylinder 3003 and the mast hydraulic cylinder 3004 of the rotary drilling rig;
an oil supply port of the hydraulic oil supply source 400 is connected to oil inlets of respective control modules of the first, second, and third motion control valve groups 100, 200, and 300 through an oil supply pipe 504, so as to supply hydraulic oil to respective modules of the respective valve groups;
the oil return ports of the control components of the first action control valve group 100, the second action control valve group 200 and the third action control valve group 300 are all connected to the oil return tank 900 through an oil return header pipe 604, so as to realize the return transmission of hydraulic oil;
any one of the main winch control assembly 101, the power head rotation control assembly 102, the auxiliary winch control assembly 201, the amplitude variation control assembly 202, the left walking control assembly 203, the right walking control assembly 204, the rotation positioning control assembly 301, the pressurization control assembly 302, the track widening control assembly 303 and the mast control assembly 304 comprises an electro-hydraulic proportional valve, a first working oil port and a second working oil port of the electro-hydraulic proportional valve are a first working oil port and a second working oil port of the control assembly where the electro-hydraulic proportional valve is located, the first working oil port and the second working oil port of each control assembly are respectively connected with an oil inlet and an oil return port of a load (a hydraulic pump or a hydraulic cylinder) connected with the electro-hydraulic proportional valve, for example, when the control assembly is a main hoisting control assembly, a first working oil port and a second working oil port of an electro-hydraulic proportional valve of the control assembly are respectively connected with an oil inlet and an oil return port of a main hoisting hydraulic pump, and the structure shown in fig. 3 can be regarded as a structural arrangement of the main hoisting control assembly, wherein a first working oil port a and a second working oil port B of the electro-hydraulic proportional valve 7101 are respectively connected with an oil inlet and an oil return port of a main hoisting hydraulic pump 1001, in the structure shown in the figure, when the electro-hydraulic proportional valve 7101 is matched with other valve body structures to form a first kind of control assembly structure, driving ends A1 and B1 are led out, and two driving ends are connected with a load (such as the main hoisting hydraulic pump); an oil inlet P and an oil return port T of the electro-hydraulic proportional valve are respectively connected with an oil inlet pipeline 500-1 and an oil return pipeline 600-1 of an action control valve set where the control assembly is located.
It should be noted that the utility model provides a first, two, three action control valves have independent oil inlet pipe respectively to hydraulic oil distribution to each control assembly that will get into through this pipeline, simultaneously, also have independent oil return pipe separately. For example, as shown in fig. 1 and fig. 2, the first motion control valve set 100 has an oil inlet pipe 501 and an oil return pipe 601, the second motion control valve set 200 has an oil inlet pipe 502 and an oil return pipe 602, and the third motion control valve set 300 has an oil inlet pipe 503 and an oil return pipe 603. And the diameter of the oil inlet pipe 501 can be set to be larger than the diameters of the oil inlet pipe 502 and the oil inlet pipe 503; the hydraulic oil supply source 400 is connected to each oil inlet pipe through a pipe 504 and then supplies hydraulic oil to each valve group. The oil return pipe of each action control valve set is connected with the oil return tank through an oil return header pipe 604.
The utility model discloses an each control assembly has following four types according to the difference of structure setting, wherein, main hoist control assembly 101, unit head control assembly 102, left side walking control assembly 203, right side walking control assembly 204 adopts the structure setting of first type control assembly, vice hoist control assembly 201, become width of cloth control assembly 202 and adopt the structure setting of second type control assembly, gyration positioning control assembly 301, track width of cloth control assembly 303, mast control assembly 304 adopts the structure setting of third type control assembly, pressurization control assembly 304 then is fourth type control assembly.
As shown in fig. 3, the structural arrangement of the first type of control assembly is as follows:
the control assembly comprises an electro-hydraulic proportional valve 7101, and further comprises a pressure compensation valve 7103 and a shuttle valve 7104, wherein the pressure compensation valve 7103 is connected between an oil inlet P of the electro-hydraulic proportional valve 7101 and an oil inlet pipeline 500-1;
two oil inlets of the shuttle valve 7104 are respectively connected between a first working oil port A and a second working oil port B of the electro-hydraulic proportional valve 7101;
an overflow valve 71021 is arranged between a first working oil port A and an oil return port T of the electro-hydraulic proportional valve 7101, an overflow valve 71022 is arranged between a second working oil port B and the oil return port T, and an overflow valve 71023 is arranged between oil outlets of a pressure compensation valve 7103 and a shuttle valve 7104. The overflow valves 71021 and 71022 can limit the maximum load in the action direction when being blocked or influenced by other blocking factors in the action process of the corresponding control structure, and the static overload safety protection function is achieved. The overflow valve 71023 is used to limit the inlet-outlet pressure difference value of the pressure compensating valve 7103 to be maintained at a constant value or within a constant range. In a general pressure compensation structure (for example, the right-side portion of the label structure of the relief valve 74023 in the structure shown in fig. 6) is provided with a spring, the restriction effect of the pressure compensation structure (for example, the right-side portion of the label structure of the relief valve 74023 in the structure shown in fig. 6) is realized by the spring, the flow capacity of the application scene corresponding to the structure is smaller, the flow capacity of the application scene corresponding to the first type of control assembly is larger (that is, the flow capacity of the pressure compensation valve 7103 is larger), at this time, if the relief valve 74023 shown in fig. 6 is adopted as the pressure compensation structure, the corresponding action area is larger, the spring realizes higher restoring force, and the relevant size of the spring is larger accordingly (for example, the wire diameter of the coil spring, that the spring becomes thicker, and even the external size/external diameter of the whole spring is difficult to increase), not only is the spring manufactured, but also the installation environment is greatly limited, that is difficult to provide a proper installation space in the existing use scene. Therefore, a combined structure of the pressure compensation valve 7103 and the overflow valve 71023 is adopted, so that a pressure compensation structure under a large-flow scene can be realized.
An oil return port T of the electro-hydraulic proportional valve 7101 is connected with an oil return pipeline 600-1.
The control component is led out of a driving end A1 and a driving end B1 and is used for connecting loads, such as a main hoisting hydraulic pump 1001, a power head rotation control component 102, a left walking hydraulic pump 2003 and a right walking hydraulic pump 2004.
As shown in fig. 4, the structural arrangement of the second type of control assembly is as follows:
an overflow valve 72021 is arranged between a first working oil port A and an oil return port T of an electro-hydraulic proportional valve 7201 of the control assembly, and an overflow valve 72022 is arranged between a second working oil port B and the oil return port T. The overflow valves 72021 and 72022 can limit the maximum load in the action direction when the corresponding control structure is blocked or influenced by other blocking factors in the action process, and the static overload safety protection function is realized.
An oil inlet P of the electro-hydraulic proportional valve 7201 is connected with an oil inlet pipeline 500-2, and an oil return port T is connected with an oil return pipeline 600-2.
The control assembly is led out of a driving end A2 and a driving end B2 and is used for connecting loads, such as an auxiliary hoisting hydraulic pump 2001 and a hoisting hydraulic cylinder 2002.
As shown in fig. 5, the structural arrangement of the third type of control assembly is as follows:
the control assembly further comprises a shuttle valve 7303, two oil inlets of the shuttle valve 7303 are respectively connected between a first working oil port A and a second working oil port B of an electro-hydraulic proportional valve 7301 of the control assembly,
an overflow valve 73021 is arranged between the first working oil port A and the oil return port T of the electro-hydraulic proportional valve 7301, and an overflow valve 73022 is arranged between the second working oil port B and the oil return port T. The overflow valves 73021 and 73022 can limit the maximum load in the action direction when being blocked or influenced by other blocking factors in the action process of the corresponding control structure, and the static overload safety protection function is achieved.
The electro-hydraulic proportional valve 7301 is connected with an oil inlet pipeline 500-3 through an overflow valve 73023, and an overflow valve 73023 is also connected with an oil outlet of a shuttle valve 7303.
An oil return port T of the electro-hydraulic proportional valve 7301 is connected with an oil return pipeline 600-3.
The control assembly is led out of a driving end A3 and a driving end B3 and is used for connecting loads, such as a rotary positioning hydraulic pump 3001, a track widening hydraulic cylinder 3003 and a mast hydraulic cylinder 3004.
As shown in fig. 6, the structural arrangement of the fourth type of control assembly is as follows:
the control component comprises a shuttle valve 7403, two oil inlets of the shuttle valve 7403 are respectively connected with a first working oil port A and a second working oil port B of an electro-hydraulic proportional valve 7401,
an overflow valve 74021 is arranged between a first working oil port A and an oil return port T of the electro-hydraulic proportional valve 7401, and overflow valves 74022 are arranged between a second working oil port B and the oil return port T, wherein the overflow valves 74021 and the overflow valves 74022 can limit the maximum load in the action direction when the drill rod is blocked in the working process (including drilling and lifting directions) or influenced by other blocking factors (for example, pressure impact is caused by oil cylinder shaking), and a static overload safety protection function is achieved.
An oil inlet P of the electro-hydraulic proportional valve 7401 is connected with an oil inlet pipeline 600-4 through an overflow valve 74023,
the oil outlet of the shuttle valve 7403 is connected with the oil return port T of the electro-hydraulic proportional valve 7401 through an overflow valve 74024, and the oil outlet of the shuttle valve 7403 is also connected with an overflow valve 74023. When the overflow valve 74023 is used for enabling a mechanism controlled by a corresponding control structure to act, the action speed of the overflow valve 74023 corresponds to the action opening (valve port opening) of the electro-hydraulic proportional valve 7401, for example, the structure correspondingly controlled by the control component is a drill rod, and the extension speed of the drill rod is only influenced by the valve port opening of the proportional valve 7401 but not influenced by a load (such as a harder rock layer) under the action of the overflow valve 74023. Without the relief valve 74023, when the drill rod is working on a hard or soft working surface, the extension or retraction speed is limited by the hardness of the working surface (e.g., when the working surface is soft, the drill rod will reach the bottom, while when the working surface is hard, the drilling speed may be slow or even immobile).
This type of control assembly leads out a drive end A4 and a drive end B4 for connection to a load, such as a pressurized hydraulic cylinder 3002.
As shown in fig. 1, the hydraulic oil supply source 400 of the present invention includes a variable displacement pump, through which the first motion control valve group 100, the second motion control valve group 200 and the third motion control valve group 300 are supplied with hydraulic oil. When in connection, the oil supply port of the variable displacement plunger pump is connected with the oil inlet pipeline 501 of the first action control valve group 100, the oil inlet pipeline 502 of the second action control valve group 200 and the oil inlet pipeline 503 of the third action control valve group 300 through the pipeline 504. The oil return pipe 601 of the first motion control valve group 100, the oil return pipe 602 of the second motion control valve group 200, and the oil return pipe 603 of the third motion control valve group 300 are connected to the oil return tank 900 through the oil return header 604, and then the oil return tank 900 is connected to the hydraulic oil supply source 400 to supply oil to the variable displacement plunger pump.
As shown in fig. 2, the hydraulic oil supply source 400 of the present invention employs a dual variable displacement plunger pump to realize two-way oil supply, so as to ensure stable oil supply. With this configuration, the first path of the oil is supplied to one end of the oil inlet pipeline of the first motion control valve group 100 (the right end oil inlet of the oil inlet pipeline 501 of the first motion control valve group 100 in the illustrated structure) and the second motion control valve group 200 (the left end oil inlet of the oil inlet pipeline 502 of the second motion control valve group 200 in the illustrated structure), and the second path of the oil is supplied to the third motion control valve group 300 (the left end oil inlet of the oil inlet pipeline 503 of the third motion control valve group 300 in the illustrated structure) and the first motion control valve group 100 (the left end oil inlet of the oil inlet pipeline 501 of the first motion control valve group 100 in the illustrated structure). At this time, the proportional pressure reducing valve 103 is disposed between the power head rotation assembly 102 and the first oil supply port of the hydraulic oil supply source 400, that is, on the pipe connection layout (of the control valve block), the proportional pressure reducing valve is closer to the hydraulic oil supply source 400 than to the other assemblies (the main winding assembly and the power head rotation assembly) of the first motion control valve group 100;
the utility model discloses in, as shown in fig. 2, first action control valves 100 includes proportional pressure reducing valve 103, oil inlet pipe 501 is connected to proportional pressure reducing valve 103's oil inlet, the oil return opening passes through return branch pipe 605 and connects oil return tank 900, proportional pressure reducing valve 103's working fluid port (pressure regulating opening) connects the control oil export of hydraulic oil supply source 400 through control oil pipe 505, because fig. 2 shows to adopt pair variable plunger pump structure in the structure, two tunnel connections two plunger pumps respectively when being connected to hydraulic oil supply source are distinguished to proportional pressure reducing valve 103's control oil pipe 505.
The utility model discloses according to the type difference of digging the rig soon in the in-service use, third action valve unit 300 can include two at least mast control assembly. In the configuration shown in FIG. 2, the third motion control valve block 300 includes two mast control assemblies, respectively a mast control assembly 304 and another mast control assembly 3004-1, which are coupled to a mast hydraulic cylinder 3004 and another mast hydraulic cylinder 3004-1, respectively.
The utility model discloses when implementing, to main hoist and gyration location need higher control accuracy in some occasions, can set up according to following structure this moment:
an electro-hydraulic proportional valve of the main winch control assembly is connected with a displacement sensor so as to monitor the opening of a valve port in real time and improve the winch precision; the structure shown in fig. 3 can be regarded as a structural arrangement of the main hoisting control assembly, wherein the electro-hydraulic proportional valve 7101 is connected with the displacement sensor 801.
An electro-hydraulic proportional valve of the rotary positioning control assembly is connected with another displacement sensor so as to monitor the opening of a valve port in real time and improve the rotary precision; the structure shown in fig. 5 can be regarded as a structural arrangement of a rotary positioning control assembly, in which an electro-hydraulic proportional valve 7301 is connected to a displacement sensor 802.
To sum up, the utility model discloses a set up three action control valves, each control assembly to digging the rig soon carries out rational planning, it is first, two, three action control valves plan the back according to each subassembly required pressure size (pipeline flow size), join in marriage the control assembly that pipeline flow is close together, for example main hoist control and the unit head gyration (unit head drive drilling rod and drilling tool) that will need great hydraulic power realize control by relatively independent first action control valves, with this rational planning flow distribution, alleviate the fuel feeding load of hydraulic oil supply source, improve the pipeline transport efficiency, stability when also increasing the pipeline infusion.
The basic principles and the main features of the invention and the advantages of the invention have been shown and described above. It will be understood by those skilled in the art that the present invention is not limited to the above embodiments, and that the foregoing embodiments and descriptions are provided only to illustrate the principles of the present invention without departing from the spirit and scope of the present invention. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (10)
1. A proportional combined valve structure suitable for a rotary drilling rig comprises a valve main body, a hydraulic oil supply source and an oil return tank, wherein the hydraulic oil supply source is connected with the valve main body, each hydraulic pump and each hydraulic cylinder for working of the rotary drilling rig are connected with the valve main body, an oil inlet and an oil outlet of the oil return tank are respectively connected with the valve main body and the hydraulic oil supply source, the proportional combined valve structure is characterized in that the valve main body comprises a first action control valve group, a second action control valve group and a third action control valve group, wherein,
the first action control valve group comprises a main winch control assembly and a power head rotation control assembly, the main winch control assembly is connected with a main winch hydraulic pump of the rotary drilling rig, and the power head rotation control assembly is connected with a power head rotation hydraulic pump of the rotary drilling rig;
the second action control valve group comprises an auxiliary hoisting control assembly, a variable amplitude control assembly, a left walking control assembly and a right walking control assembly, and the auxiliary hoisting control assembly, the variable amplitude control assembly, the left walking control assembly and the right walking control assembly are respectively connected with an auxiliary hoisting hydraulic pump, a variable amplitude hydraulic cylinder, a left walking hydraulic pump and a right walking hydraulic pump of the rotary drilling rig;
the third action control valve bank comprises a rotary positioning control assembly, a pressurization control assembly, a crawler broadening control assembly and a mast control assembly, wherein the rotary positioning control assembly, the pressurization control assembly, the crawler broadening control assembly and the mast control assembly are respectively connected with a rotary positioning hydraulic pump, a pressurization hydraulic cylinder, a crawler broadening hydraulic cylinder and a mast hydraulic cylinder of the rotary drilling rig;
an oil supply port of the hydraulic oil supply source is connected with oil inlets of control assemblies of the first action control valve group, the second action control valve group and the third action control valve group;
the oil return ports of the control components of the first action control valve group, the second action control valve group and the third action control valve group are connected to the oil return tank;
any control assembly comprises an electro-hydraulic proportional valve, a first working oil port and a second working oil port of the electro-hydraulic proportional valve are a first working oil port and a second working oil port of the control assembly where the electro-hydraulic proportional valve is located, and the first working oil port and the second working oil port of each control assembly are respectively connected with an oil inlet and an oil return port of a load connected with the first working oil port and the second working oil port;
and an oil inlet and an oil return port of the electro-hydraulic proportional valve are respectively connected with an oil inlet pipeline and an oil return pipeline of the action control valve group where the control assembly is located.
2. The proportional combination valve structure of claim 1, wherein any one of the main winding control assembly, the power head control assembly, the left travel control assembly and the right travel control assembly further comprises a pressure compensation valve and a shuttle valve,
the pressure compensation valve is connected between an oil inlet of the electro-hydraulic proportional valve of the control assembly and an oil inlet pipeline of the action control valve group where the pressure compensation valve is located;
two oil inlets of the shuttle valve are respectively connected between a first working oil port and a second working oil port of the electro-hydraulic proportional valve;
overflow valves are arranged between a first working oil port and an oil return port of the electro-hydraulic proportional valve, between a second working oil port and the oil return port, and between the pressure compensation valve and an oil outlet of the shuttle valve.
3. The proportional combination valve structure suitable for the rotary drilling rig according to claim 1, wherein overflow valves are arranged between the first working oil port and the oil return port, and between the second working oil port and the oil return port of the electro-hydraulic proportional valve of any one of the auxiliary winch control assembly and the amplitude variation control assembly.
4. The proportional combination valve structure of claim 1, wherein any one of the rotary positioning control assembly, the track broadening control assembly, and the mast control assembly further comprises a shuttle valve,
two oil inlets of the shuttle valve are respectively connected between a first working oil port and a second working oil port of the control assembly,
overflow valves are arranged between a first working oil port and an oil return port and between a second working oil port and the oil return port of an electro-hydraulic proportional valve of the control assembly;
the electro-hydraulic proportional valve is connected with an oil inlet pipeline of the action control valve group where the control assembly is located through another overflow valve, and the other overflow valve is also connected with an oil outlet of the shuttle valve.
5. The proportional combination valve structure suitable for the rotary drilling rig according to claim 1, wherein the pressurization control assembly is arranged as follows:
the pressurization control assembly comprises a shuttle valve, two oil inlets of the shuttle valve are respectively connected with a first working oil port and a second working oil port of an electro-hydraulic proportional valve of the pressurization control assembly,
a first overflow valve is arranged between the first working oil port and the oil return port of the electro-hydraulic proportional valve and between the second working oil port and the oil return port,
an oil inlet of the electro-hydraulic proportional valve is connected with an oil inlet pipeline of the third action control valve group through a second overflow valve,
the oil outlet of the shuttle valve is connected with the oil return port of the electro-hydraulic proportional valve through a third overflow valve, and the oil outlet of the shuttle valve is connected with the second overflow valve.
6. The proportional combination valve structure suitable for a rotary drilling rig according to claim 1, wherein the hydraulic oil supply source comprises a variable displacement piston pump.
7. The proportional combination valve structure suitable for the rotary drilling rig according to claim 1, wherein the hydraulic oil supply source is a dual variable plunger pump.
8. The proportional combination valve structure suitable for a rotary drilling rig according to claim 7, wherein the first action control valve set comprises a proportional pressure reducing valve, an oil inlet and an oil return port of the proportional pressure reducing valve are respectively connected with the hydraulic oil supply source and the oil return tank, and a working oil port of the proportional pressure reducing valve is connected with a control oil outlet of the hydraulic oil supply source.
9. The structure of any one of claims 1 to 8, wherein the third set of motion control valves comprises at least two mast control assemblies.
10. The proportional combination valve structure suitable for the rotary drilling rig according to any one of claims 1 to 8, wherein the electro-hydraulic proportional valve of the main winch control assembly is connected with a displacement sensor;
and the electro-hydraulic proportional valve of the rotary positioning control assembly is connected with another displacement sensor.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222472189.7U CN218235646U (en) | 2022-09-19 | 2022-09-19 | Proportional combination valve structure suitable for rotary drilling rig |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222472189.7U CN218235646U (en) | 2022-09-19 | 2022-09-19 | Proportional combination valve structure suitable for rotary drilling rig |
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| CN218235646U true CN218235646U (en) | 2023-01-06 |
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| CN202222472189.7U Active CN218235646U (en) | 2022-09-19 | 2022-09-19 | Proportional combination valve structure suitable for rotary drilling rig |
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| Country | Link |
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