CN113864277A - Check valve, flow overload protection hydraulic system and operation machine - Google Patents
Check valve, flow overload protection hydraulic system and operation machine Download PDFInfo
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- CN113864277A CN113864277A CN202111274752.3A CN202111274752A CN113864277A CN 113864277 A CN113864277 A CN 113864277A CN 202111274752 A CN202111274752 A CN 202111274752A CN 113864277 A CN113864277 A CN 113864277A
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- 230000006835 compression Effects 0.000 claims description 30
- 238000007906 compression Methods 0.000 claims description 30
- 230000000712 assembly Effects 0.000 claims 1
- 238000000429 assembly Methods 0.000 claims 1
- 239000003921 oil Substances 0.000 description 123
- 239000010720 hydraulic oil Substances 0.000 description 30
- 230000008093 supporting effect Effects 0.000 description 15
- 238000006073 displacement reaction Methods 0.000 description 12
- 238000000034 method Methods 0.000 description 11
- 239000007788 liquid Substances 0.000 description 10
- 230000009286 beneficial effect Effects 0.000 description 8
- 238000009795 derivation Methods 0.000 description 8
- 238000005336 cracking Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000001771 impaired effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Check Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a check valve, a flow overload protection hydraulic system and an operation machine, wherein the check valve comprises: a valve body; a valve spool is arranged in the valve body, and the valve spool can be switched between a closed position and a full-open position; an elastic component arranged in the valve body and acting on the valve core to enable the valve core to generate the trend of moving from the full-open position to the closed position; wherein when the valve core is positioned between the closed position and the first position, the elastic coefficient of the elastic component is K1Said first position being between said closed position and said fully open position; when the valve core is positioned between the first position and the full open position, the elastic coefficient of the elastic component is K2And K is2＞K1. By the arrangement, the check valve, the flow overload protection hydraulic system and the operation machine, provided by the invention, can effectively avoid instantaneous increase of oil pressureLeading to the problem of damage to the functional components.
Description
Technical Field
The invention relates to the technical field of hydraulic pressure, in particular to a one-way valve, an overload protection hydraulic system and an operation machine.
Background
The hydraulic oil of operation machinery can produce high temperature at the course of the work, in order to carry out rapid cooling to high temperature hydraulic oil, among the prior art, is provided with the hydraulic oil radiator usually. However, hydraulic oil has a high pressure, and in order to avoid damage to the hydraulic oil radiator caused by the hydraulic oil in a high-pressure state, a hydraulic oil radiator flow overload protection device is arranged in the prior art.
The hydraulic oil radiator flow overload protection device in the prior art comprises two hydraulic one-way valves connected in parallel, the two one-way valves have different opening pressures, a first one-way valve with a smaller opening pressure is connected with the hydraulic oil radiator in series, a second one-way valve with a larger opening pressure is arranged on an oil return path, and the oil return path is directly connected with an oil return tank. When the radiator works, when the oil return pressure exceeds the opening pressure of the first check valve, the first check valve is opened, oil return passes through the radiator, when the oil return pressure is gradually increased, the second check valve is opened, the oil return directly enters the oil tank, and therefore the radiator is prevented from cracking due to flow overload.
However, when the excavator is in working conditions such as crushing, the oil return flow is changed in a pulse mode, the first check valve is opened, the oil return passes through the radiator, the oil return flow is rapidly increased and reaches the maximum instantly, the second check valve is not opened in time, the instantaneous flow passing through the first check valve is large at the moment and possibly exceeds the maximum flow capable of being borne by the functional component (hydraulic oil radiator), and the functional component is damaged and cracked.
Therefore, how to avoid the damage of the functional components caused by the instantaneous increase of the oil pressure becomes an important technical problem to be solved by those skilled in the art.
Disclosure of Invention
The invention provides a check valve, a flow overload protection hydraulic system and an operating machine, which can effectively avoid the problem of damage to functional components caused by instantaneous increase of oil pressure.
A first aspect of the present invention provides a one-way valve comprising:
a valve body;
a spool disposed within the valve body and switchable between a closed position and a fully open position;
an elastic component arranged in the valve body and acting on the valve core to enable the valve core to generate the trend of moving from the full-open position to the closed position; wherein,
the valve core is positioned at the closed positionBetween the first position and the second position, the elastic component has an elastic coefficient K1Said first position being between said closed position and said fully open position;
when the valve core is positioned between the first position and the full open position, the elastic coefficient of the elastic component is K2And K is2＞K1。
According to the one-way valve provided by the invention, the elastic assembly comprises a first elastic part and a second elastic part, and when the valve core is positioned between the closed position and the first position, the first elastic part acts on the valve core; when the valve core is positioned between the first position and the full-open position, the first elastic piece and the second elastic piece jointly act on the valve core.
According to the one-way valve provided by the invention, the second elastic piece is arranged as a compression elastic piece, and when the valve core is positioned between the first position and the full-open position, the second elastic piece can generate compression deformation which enables the valve core to generate a trend of moving towards the closed position.
According to the one-way valve provided by the invention, the first elastic piece is arranged as a compression elastic piece, and when the valve core is positioned between the full-open position and the closed position, the first elastic piece can generate compression deformation which enables the valve core to generate a trend of moving towards the closed position.
According to the one-way valve provided by the invention, the first elastic piece is arranged as a tensile elastic piece, and when the valve core is positioned between the full-open position and the closed position, the first elastic piece can generate tensile deformation which enables the valve core to generate a trend of moving towards the closed position.
According to the check valve provided by the invention, the first elastic piece and the second elastic piece are compression springs, the second elastic piece is accommodated in a cavity of the first elastic piece, and when the valve core is positioned between the first position and the full-open position, the first elastic piece and the second elastic piece are arranged in parallel.
The second aspect of the invention provides a flow overload protection hydraulic system, which comprises a first oil path, wherein a functional component and a first one-way valve are arranged on the first oil path, an oil outlet of the first one-way valve is communicated with an oil inlet of the functional component, and the first one-way valve is any one of the one-way valves.
The flow overload protection hydraulic system further comprises a second oil way, wherein the oil inlet end of the second oil way is communicated with the oil inlet end of the first oil way, and the oil outlet end of the second oil way is communicated with the oil outlet end of the first oil way; wherein,
the second oil way is provided with a second one-way valve, the conduction direction of the second one-way valve is consistent with the direction from the oil inlet end to the oil outlet end of the second oil way, and the opening pressure of the second one-way valve is greater than that of the first one-way valve.
According to the flow overload protection hydraulic system provided by the invention, the first check valve and/or the second check valve are/is provided with an adjusting device capable of adjusting the elasticity of the elastic component of the first check valve and/or the second check valve, and the flow overload protection hydraulic system further comprises:
the pressure sensor is used for sensing the pressure of the oil inlet of the functional component;
and the controller is used for controlling the adjusting device according to the oil inlet pressure of the functional component.
According to the flow overload protection hydraulic system provided by the invention, the first check valve and the second check valve are both set as hydraulic control check valves, and the flow overload protection hydraulic system further comprises:
the first hydraulic control oil way is communicated with a hydraulic control input end of the first one-way valve and is communicated with an oil inlet of the functional component, and the first hydraulic control oil way can control the elasticity of an elastic component of the first one-way valve according to the pressure of the oil inlet of the functional component; and/or the presence of a gas in the gas,
and the second hydraulic control oil way is communicated with a hydraulic control input end of the second one-way valve and is communicated with the oil inlet of the functional component, and the second hydraulic control oil way can control the elasticity of the elastic component of the second one-way valve according to the pressure of the oil inlet of the functional component.
A third aspect of the invention provides a work machine comprising a flow overload protection hydraulic system as defined in any one of the preceding claims.
The invention provides a one-way valve which comprises a valve body, a valve core and an elastic assembly, wherein the valve core is arranged in the valve body and can be switched between a closed position and a full-open position, when the valve core is in the closed position, the one-way valve is in a closed state, when the valve core is in the full-open position, the one-way valve is in a maximum-opening state, and the elastic assembly is supported on the valve core. When the liquid inlet pressure of the one-way valve is smaller than the supporting force of the elastic component, the valve core is in the closed position, and when the liquid inlet pressure of the one-way valve is larger than the supporting force of the elastic component, the valve core gradually displaces towards the full-open position direction along with the increase of the liquid inlet pressure, so that the opening degree of the one-way valve gradually increases.
It should be noted that, according to the technical scheme provided by the invention, when the valve core is located between the closed position and the first position, the elastic coefficient of the elastic component is K1The first position is located between the closed position and the fully open position; when the valve core is positioned between the first position and the full open position, the elastic coefficient of the elastic component is K2And K is2＞K1。
So set up, there is feed liquor pressure when the check valve to feed liquor pressure is greater than the cracking pressure of case, and the case is opened by closed position to the displacement of first position direction, and the distance between first position and the closed position is L, and the case is by the in-process of closed position to the displacement of first position direction, and the elastic component's that the case received holding power F ═ K1X and X are deformation quantities of the elastic component. When the liquid inlet pressure of the one-way valve is increased instantly, the valve core is rapidly displaced to the full open position, and when the liquid inlet pressure is displaced to the position between the first position and the full open position, the elastic coefficient of the elastic component is changed into K2At this time, the valve core receives a supporting force F ═ K of the elastic component1L+K2(X-L), the supporting force borne by the valve core can be obviously improved, and the valve core can be prevented from being rapidly opened to a full-open position, so that the problem that the flow is suddenly increased to damage functional parts is solved.
Secondly, in a further scheme provided by the invention, the elastic assembly comprises a first elastic part and a second elastic part, and when the valve core is positioned between the closed position and the first position, the first elastic part acts on the valve core; when the valve core is positioned between the first position and the full-open position, the first elastic piece and the second elastic piece jointly act on the valve core.
So set up, under the effect of hydraulic pressure was advanced to the check valve, the case was by closed position to the displacement of full open position direction, and when the feed liquor pressure of check valve was within normal range, the case was located between closed position and the first position, and the case relies on the supporting role of first elastic component. When the feed liquor pressure of check valve increases instantaneously, under the effect of feed liquor pressure, the case displacement to first position and open position entirely between, at this moment, the case receives the common supporting role of first elastic component and second elastic component, can effectively prevent that the case from receiving the effect that feed liquor pressure increases instantaneously and opening completely, and then leads to the impaired problem of functional unit of low reaches. This setting mode is provided with two elastic component, and simple structure is reliable.
The invention further provides a flow overload protection hydraulic system which comprises a first oil way, wherein the first oil way is provided with a functional component and a first one-way valve, an oil outlet of the first one-way valve is communicated with an oil inlet of the functional component, and the first one-way valve is the one-way valve.
By the arrangement, the flow overload protection hydraulic system provided by the invention has the advantages that the check valve can effectively protect the downstream functional components, and the problem that the functional components are damaged due to the instantaneous increase of the hydraulic flow is solved. The derivation process of the beneficial effect is substantially similar to the derivation process of the beneficial effect brought by the check valve, and is not described herein again.
Fourthly, in a further technical scheme, the oil-saving device further comprises a second oil way, wherein the oil inlet end of the second oil way is communicated with the oil inlet end of the first oil way, the oil outlet end of the second oil way is communicated with the oil outlet end of the first oil way, and namely the first oil way and the second oil way form a parallel oil way. In addition, the second oil circuit is provided with a second one-way valve, the conduction direction of the second one-way valve is consistent with the direction from the oil inlet end to the oil outlet end of the second oil circuit, and the opening pressure of the second one-way valve is greater than that of the first one-way valve.
It should be noted that the second oil path is a pressure relief oil path, and when the pressure of the hydraulic oil is within a normal range, the first check valve is turned on, and the hydraulic oil flows through the functional component. When the pressure of the hydraulic oil is increased instantaneously, the elastic assembly is arranged in the first one-way valve, so that the problem that the downstream functional parts are damaged due to the fact that the first one-way valve is opened completely and the flow is increased suddenly can be avoided. And when the pressure of the hydraulic oil is larger, the second check valve is opened, and the pressure is relieved through the second oil path.
The invention further provides a working machine which comprises the flow overload protection hydraulic system. With the arrangement, the working machine provided by the invention can effectively avoid the problem that the functional components are damaged due to the instantaneous increase of the oil pressure. The derivation process of the beneficial effect is substantially similar to the derivation process of the beneficial effect of the flow overload protection hydraulic system, and is not described herein again.
Drawings
In order to more clearly illustrate the technical solutions of the present invention or the prior art, the drawings needed for the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and those skilled in the art can also obtain other drawings according to the drawings without creative efforts.
FIG. 1 is a schematic view of a check valve in an embodiment of the present invention;
FIG. 2 is a schematic diagram of a flow overload protection hydraulic system in an embodiment of the invention;
FIG. 3 is a schematic diagram showing the relationship between the elastic force and the deformation amount of the elastic member according to the embodiment of the present invention;
FIG. 4 is a schematic diagram of another flow overload protection hydraulic system according to an embodiment of the present invention;
11: a valve body; 12: a valve core; 13: a first elastic member;
14: a second elastic member; 15: an elastic component; 16: a first check valve;
17: a second one-way valve; 18: a first oil passage; 19: a second oil passage;
20: a hydraulic oil radiator; 21: an oil return tank; 22: a first hydraulic control oil path;
23: and a second hydraulic control oil path.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
A check valve, a flow overload protection hydraulic system, and a work machine according to embodiments of the present invention will be described with reference to fig. 1 to 3.
Referring to fig. 1, the check valve provided in this embodiment includes a valve body 11, a valve core 12 and an elastic component 15, where the valve core 12 is disposed in the valve body 11, the valve core 12 can be switched between a closed position and a fully opened position, when the valve core 12 is in the closed position, the check valve is in a closed state, and when the valve core 12 is in the fully opened position, the check valve is in a maximum opening state, and the elastic component 15 is supported on the valve core 12. When the liquid inlet pressure of the one-way valve is smaller than the supporting force of the elastic component 15, the valve core 12 is in the closed position, and when the liquid inlet pressure of the one-way valve is larger than the supporting force of the elastic component 15, the valve core 12 gradually displaces towards the full-open position direction along with the increase of the liquid inlet pressure, so that the opening degree of the one-way valve gradually increases.
It should be noted that, according to the technical solution provided in this embodiment, when the valve core 12 is located between the closed position and the first position, the elastic coefficient of the elastic component 15 is K1The first position is located between the closed position and the fully open position; when the valve core 12 is positioned between the first position and the full opening position, the elastic coefficient of the elastic component 15 is K2And K is2＞K1。
So set up, when the check valve has feed liquor pressure to feed liquor pressure is greater than the cracking pressure of case 12, case 12 is opened by closed position to the displacement of first position direction, and the distance between first position and the closed position is L, and case 12 is by the in-process of closed position to the displacement of first position direction, and the supporting force F of elastic component 15 that case 12 received is K1X, X are the deformation amounts of the elastic member 15. When the liquid inlet pressure of the one-way valve is increased instantly, the valve core 12 is rapidly displaced to the full open position, and when the liquid inlet pressure is displaced to the position between the first position and the full open position, the elastic coefficient of the elastic component 15 is changed into K2At this time, the supporting force F of the elastic member 15 received by the valve body 12 is K1L+K2(X-L), as shown in fig. 3, it can be seen that the supporting force applied to the valve element 12 can be significantly increased, and thus the valve element 12 can be prevented from being rapidly opened to the fully open position, which causes a problem that the flow suddenly increases to damage the functional components.
In a further embodiment, the elastic assembly 15 comprises a first elastic element 13 and a second elastic element 14, the first elastic element 13 acting on the spool 12 when the spool 12 is between the closed position and the first position; when the valve core 12 is located between the first position and the full open position, the first elastic element 13 and the second elastic element 14 jointly act on the valve core 12.
Specifically, the length of the first elastic member 13 is greater than the length of the second elastic member 14, and when the valve body 12 is in the closed position, the first elastic member 13 acts on the valve body 12, while the second elastic member 14 does not act on the valve body 12. When the spool 12 moves from the closed position to the first position, the spool 12 is subjected to the elastic force of the first elastic member 13, and the amount of deformation of the first elastic member 13 gradually increases with the movement of the spool 12. When the spool 12 moves to the first position, the first elastic member 13 and the second elastic member 14 work together on the spool 12, and as the spool 12 is displaced from the first position toward the fully open position, the deformation amount of the first elastic member 13 and the second elastic member 14 gradually increases.
So set up, under the effect of the hydraulic pressure of advancing, case 12 is by closed position to the displacement of full open position direction, and when the feed liquor pressure of check valve was within normal range, case 12 was located between closed position and the first position, and case 12 receives the supporting role of first elastic component 13. When the feed liquor pressure of check valve increases instantaneously, under the effect of feed liquor pressure, case 12 displacement to first position and full open position between, at this moment, case 12 receives the common supporting role of first elastic component 13 and second elastic component 14, can effectively prevent case 12 because of feed liquor pressure increases completely, and then leads to the impaired problem of functional unit of low reaches. Two elastic pieces are arranged in the embodiment, and the structure is simple and reliable.
In some embodiments, the second elastic element 14 may be a compression elastic element, and the second elastic element 14 is capable of generating compression deformation which tends to move the valve element 12 to the closed position when the valve element 12 is located between the first position and the full-open position.
The first elastic element 13 may also be a compression elastic element, and when the valve core 12 is located between the full-open position and the closed position, the first elastic element 13 can generate compression deformation which makes the valve core 12 generate a tendency to move towards the closed position. Of course, in other embodiments, the first elastic element 13 may also be configured as a tensile elastic element, and when the valve core 12 is located between the full-open position and the closed position, the first elastic element 13 can generate tensile deformation that tends to move the valve core 12 toward the closed position. Specifically, the stretching elastic element is arranged at one end of the valve core 12 far away from the second elastic element 14; one end of the stretching elastic piece is connected with the valve core 12, the other end is connected with the valve body, and the valve core 12 is pulled through stretching force.
When both the first and second elastic members 13, 14 are arranged as compression elastic members, and when the spool 12 is between the first position and the fully open position, they are arranged in parallel. That is, one end of the first elastic element 13 elastically acts on the valve body, and the other end elastically acts on the end of the valve core 12 opposite to the valve port of the valve body 11; the second elastic member 14 may be accommodated in the cavity of the first elastic member 13, and when the valve core 12 is located between the first position and the full open position, the second elastic member 14 generates a compression deformation that moves the valve core 12 to the closed position.
The first elastic member 13 has an elastic coefficient K1The second elastic member 14 has an elastic coefficient K0During the displacement of the valve element 12 from the closed position to the first position, the valve element 12 is supported by the spring assembly 15Stretching force F ═ K1X, when the valve element 12 is displaced between the first position and the fully open position, K is the supporting force F of the elastic element 15 applied to the valve element 121X+K0(X-L)。
In a further embodiment, the first elastic member 13 is provided as a first compression spring and the second elastic member 14 is provided as a second compression spring.
In some embodiments, referring to fig. 1, the first ends of the first and second compression springs are both attached to the mounting portion of the valve body 11, which may be specifically configured as a snap groove capable of snapping over the ends of the springs. The second ends of the first compression spring and the second compression spring correspond to the valve core 12, the second end of the first compression spring always acts on the valve core 12, and under the supporting action of the first compression spring, the valve core 12 is in a closed position when no external pressure exists; the second end of the second compression spring is disposed at the first position. Specifically, in order to avoid collision between the first elastic member 13 and the second elastic member 14, the second elastic member 14 is ensured not to be displaced and to perform an elastic pushing action. The diameter of the second elastic element 14 is smaller than that of the first elastic element 13, one end of the second elastic element 14, which is far away from the valve core 12, is fixedly connected to the mounting part of the valve body 11, and the other end is in a free state and is opposite to the end part of the valve core 12.
In a further embodiment, the first compression spring has a larger coil diameter than the second compression spring, and the second compression spring is nested inside the first compression spring.
So set up, first compression spring and second compression spring are the muff-coupling relation, compact structure. Furthermore, the resultant force direction formed by the first compression spring and the second compression spring is coincident with the center of the valve core 12, and the arrangement can ensure that the valve core 12 has better stability in the movement process.
The embodiment of the invention also provides a flow overload protection hydraulic system which comprises a first oil path 18, wherein the first oil path 18 is provided with a functional component and a first one-way valve 16, an oil outlet of the first one-way valve 16 is communicated with an oil inlet of the functional component, and the first one-way valve 16 is the one-way valve in any one of the embodiments.
So set up, the flow overload protection hydraulic system that this embodiment provided, check valve can form effective protection to its functional unit of low reaches, prevents that hydraulic flow from increasing instantaneously and leading to the problem of functional unit damage. The term "downstream" means that the first passage is upstream and the second passage is downstream in the direction in which the hydraulic oil flows. The derivation process of the beneficial effect is substantially similar to the derivation process of the beneficial effect brought by the check valve, and is not described herein again.
In a further embodiment, the flow overload protection hydraulic system further comprises a second oil path 19, an oil inlet end of the second oil path 19 is communicated with an oil inlet end of the first oil path 18, and an oil outlet end of the second oil path 19 is communicated with an oil outlet end of the first oil path 18, that is, the first oil path 18 and the second oil path 19 form a parallel oil path. Further, the second oil passage 19 is provided with a second check valve 17, the direction of conduction of the second check valve 17 coincides with the direction from the oil inlet end to the oil outlet end of the second oil passage 19, and the cracking pressure of the second check valve 17 is larger than the cracking pressure of the first check valve 16.
It should be noted that the second oil passage 19 is a pressure relief oil passage, and when the pressure of the hydraulic oil is within a normal range, the first check valve 16 is opened, and the hydraulic oil flows through the functional component. When the pressure of the hydraulic oil is increased instantaneously, the elastic assembly 15 is arranged in the first check valve 16, so that the problem that the downstream functional components are damaged due to the fact that the first check valve 16 is fully opened and the flow is suddenly increased can be avoided. When the pressure of the hydraulic oil is high, the second check valve 17 opens and the pressure is released through the second oil passage 19.
In a further embodiment, the first non return valve 16 and/or the second non return valve 17 are provided with adjustment means capable of adjusting the spring force of their elastic members. The adjusting device can adjust the positions of the elastic components in the first one-way valve and the second one-way valve, and then the elastic force of the elastic components is adjusted.
In this embodiment, the flow overload protection hydraulic system further includes:
a pressure sensor (not shown in the figure) for sensing the pressure of the oil inlet of the functional component;
and a controller (not shown in the figure) for controlling the adjusting device according to the oil inlet pressure of the functional component.
When the pressure of the oil inlet of the functional component is increased, the controller can adjust the displacement of the elastic component of the first one-way valve 16 through the adjusting device, so that the elastic force of the elastic component is increased, and the opening degree of the first one-way valve 16 is reduced; and/or the controller can adjust the displacement of the elastic part of the second one-way valve 17 through the adjusting device, so that the elastic force of the elastic part is reduced, the opening degree of the second one-way valve 17 is increased, and then the pressure is released through the second one-way valve 17, thereby protecting functional parts.
The controller can control the opening degrees of the first check valve 16 and the second check valve 17 independently or can coordinate and control the first check valve 16 and the second check valve 17 at the same time. Through cooperative control, functional parts can be protected more flexibly, and reasonable circulation of the whole hydraulic oil of the flow overload protection hydraulic system is guaranteed.
In a further embodiment, the first check valve 16 and the second check valve 17 are both provided as pilot-operated check valves, i.e. the position of the internal elastic member of the first check valve 16 and the second check valve 17 can be controlled by hydraulic pressure, and the control of the opening degree of the first check valve 16 and the second check valve 17 can be realized by hydraulic pressure.
As shown in fig. 4, the flow overload protection hydraulic system further includes a first hydraulic control oil path 22 and a second hydraulic control oil path 23, wherein the first hydraulic control oil path 22 is communicated with the hydraulic control input end of the first check valve 16, the first hydraulic control oil path 22 is communicated with the oil inlet of the functional component, and the first hydraulic control oil path 22 can control the elastic force of the elastic component according to the pressure of the oil inlet of the functional component. The second hydraulic control oil path 23 is communicated with a hydraulic control input end of the second check valve 17, the second hydraulic control oil path 23 is communicated with an oil inlet of the functional component, and the second hydraulic control oil path 23 can control the opening pressure of the second check valve 17 according to the oil inlet pressure of the functional component.
So set up, when the oil inlet pressure of functional unit increases, first hydraulic control oil circuit 22 accessible hydraulic control carries drive hydraulic pressure to the hydraulic control input of first check valve 16, and then increases the hydraulic pressure in the hydraulic control cavity of seting up in the first check valve 16, then promotes the elastic component displacement, makes elastic component's elasticity increase, reduces the aperture of first check valve 16. Meanwhile, the second hydraulic control oil path 23 controls the elastic member of the second check valve 17 to move, so that the elastic force of the elastic member is reduced, the opening degree of the second check valve 17 is increased, and then the pressure is released through the second check valve 17, thereby protecting the functional components.
It should be noted that, the specific structure of the check valve that displaces through the hydraulic drive elastic component can refer to a hydraulic control check valve in the prior art, and details are not repeated here.
In some embodiments, the functional component disposed on the first oil path 18 is a hydraulic oil radiator 20, and by providing the first check valve 16 on the first oil path 18, the second oil path 19, and the second check valve 17 on the second oil path 19, the hydraulic oil radiator 20 can be effectively protected, and the problem of damage to the radiator due to excessive hydraulic oil pressure or instantaneous increase of hydraulic oil can be avoided.
Moreover, when the temperature of the hydraulic oil is low, the viscosity of the hydraulic oil is high, and the pressure of an oil inlet of the hydraulic oil radiator 20 is high, the heat loss can be reduced by reducing the flow of the hydraulic oil radiator 20, so that the whole machine can reach the optimal working temperature as soon as possible.
In a further embodiment, the oil outlet ends of the first oil passage 18 and the second oil passage 19 are both communicated with the oil return tank 21, so that the hydraulic oil flowing out of the first oil passage 18 and the second oil passage 19 can flow back to the oil return tank 21.
Embodiments of the present disclosure also provide a work machine including a flow overload protection hydraulic system as described above, which in some embodiments may be an excavator.
So set up, when the excavator was in operating mode such as breakage, because the oil return flow is the pulse variation, through the flow overload protection hydraulic system that this embodiment provided, can effectively prevent to flow through the flow rapid rising of radiator, cause the problem of damage to the radiator. The derivation process of the beneficial effect is substantially similar to the derivation process of the beneficial effect brought by the flow overload protection hydraulic system, and details are not repeated here.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (11)
1. A check valve, comprising:
a valve body;
a spool disposed within the valve body and switchable between a closed position and a fully open position;
an elastic component arranged in the valve body and acting on the valve core to enable the valve core to generate the trend of moving from the full-open position to the closed position; wherein,
when the valve core is positioned between the closed position and the first position, the elastic coefficient of the elastic component is K1Said first position being between said closed position and said fully open position;
when the valve core is positioned between the first position and the full open position, the elastic coefficient of the elastic component is K2And K is2＞K1。
2. The check valve of claim 1, wherein the spring assembly includes a first spring and a second spring, the first spring acting on the valve spool when the valve spool is between the closed position and the first position; when the valve core is positioned between the first position and the full-open position, the first elastic piece and the second elastic piece jointly act on the valve core.
3. The check valve of claim 2, wherein the second resilient member is configured as a compression spring and is capable of compressive deformation tending to move the valve element toward the closed position when the valve element is between the first position and the fully open position.
4. The check valve of claim 3, wherein the first resilient member is configured as a compression resilient member that is capable of compressive deformation tending to move the valve element toward the closed position when the valve element is between the fully open position and the closed position.
5. The check valve of claim 3, wherein the first elastic member is configured as a tensile elastic member, and when the valve element is located between the full open position and the closed position, the first elastic member is capable of generating tensile deformation that tends to move the valve element toward the closed position.
6. The check valve of claim 4, wherein the first and second resilient members are compression springs, the second resilient member is received in a cavity of the first resilient member, and the first and second resilient members are configured to be arranged in parallel when the spool is between the first position and the fully open position.
7. A flow overload protection hydraulic system is characterized by comprising a first oil path, wherein a functional component and a first one-way valve are arranged on the first oil path, an oil outlet of the first one-way valve is communicated with an oil inlet of the functional component, and the first one-way valve is the one-way valve as claimed in any one of claims 1 to 6.
8. The hydraulic system for flow overload protection according to claim 7, further comprising a second oil path, an oil inlet end of the second oil path being in communication with an oil inlet end of the first oil path, an oil outlet end of the second oil path being in communication with an oil outlet end of the first oil path; wherein,
the second oil way is provided with a second one-way valve, the conduction direction of the second one-way valve is consistent with the direction from the oil inlet end to the oil outlet end of the second oil way, and the opening pressure of the second one-way valve is greater than that of the first one-way valve.
9. Flow overload protection hydraulic system according to claim 8, characterised in that the first non return valve and/or the second non return valve are provided with adjustment means capable of adjusting the spring force of their spring assemblies, the flow overload protection hydraulic system further comprising:
the pressure sensor is used for sensing the pressure of the oil inlet of the functional component;
and the controller is used for controlling the adjusting device according to the oil inlet pressure of the functional component.
10. The flow overload protection hydraulic system of claim 8, wherein the first check valve and the second check valve are both configured as pilot operated check valves, the flow overload protection hydraulic system further comprising:
the first hydraulic control oil way is communicated with a hydraulic control input end of the first one-way valve and is communicated with an oil inlet of the functional component, and the first hydraulic control oil way can control the elasticity of an elastic component of the first one-way valve according to the pressure of the oil inlet of the functional component; and/or the presence of a gas in the gas,
and the second hydraulic control oil way is communicated with a hydraulic control input end of the second one-way valve and is communicated with the oil inlet of the functional component, and the second hydraulic control oil way can control the elasticity of the elastic component of the second one-way valve according to the pressure of the oil inlet of the functional component.
11. A work machine comprising a flow overload protection hydraulic system according to any one of claims 7 to 10.
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| CN202111274752.3A CN113864277A (en) | 2021-10-29 | 2021-10-29 | Check valve, flow overload protection hydraulic system and operation machine |
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| CN202111274752.3A CN113864277A (en) | 2021-10-29 | 2021-10-29 | Check valve, flow overload protection hydraulic system and operation machine |
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