One-way throttling hydraulic lock and method of operation thereof

Abstract

The application provides a one-way throttling hydraulic lock and a working method thereof, a valve cavity is formed in a valve body, a piston is slidably arranged in the valve cavity, the valve cavity is divided into a first cavity and a second cavity by the piston, a first working oil channel, a second working oil channel, a third working oil channel and a fourth working oil channel are formed in the valve body, the first working oil channel and the second working oil channel are connected with the first cavity, and the third working oil channel and the fourth working oil channel are connected with the second cavity; a first connecting sleeve is installed in the first cavity, the first connecting sleeve is coaxially installed with the piston, a second connecting sleeve is connected with one end of the first connecting sleeve away from the piston, an adjusting rod is coaxially installed in the first connecting sleeve and the second connecting sleeve, a conical valve sleeve is connected with one end of the adjusting rod facing the piston, a conical valve core and a spring are arranged in the conical valve sleeve, one end of the spring abuts against the adjusting rod, and one end of the spring abuts against the conical valve core, so that the functions of a hydraulic throttling valve and a hydraulic lock in the hydraulic field are integrated, the volume is small, and the point of possible external leakage is avoided.

Description

Technical Field

[0001] This invention relates to the field of hydraulic valve technology, and in particular to a one-way throttling hydraulic lock and its working method. Background Technology

[0002] Currently, hydraulic transmission and control technology is widely used in heavy equipment such as industrial hydraulic systems. Among them, as key hydraulic components, stacked one-way throttle valves and stacked hydraulic locks are widely used in the working speed control and load holding circuits of hydraulic actuators. Stacked one-way throttle valves, such as... Figure 1 As shown, this is a hydraulic valve that changes the flow rate of hydraulic oil from A1 to A or from B1 to B by controlling the size of the annular flow area between the valve core ① and the valve body ②; a stacked hydraulic lock, such as... Figure 2 As shown, this is a hydraulic valve with valve body ①, check valve ②, and control piston ③ as its main components. When piston ③ has no thrust, check valve ② can prevent hydraulic oil in channel A1 from flowing to A, or prevent hydraulic oil in channel B1 from flowing to B; while the flow of hydraulic oil from channel A to channel A1, or the flow of hydraulic oil from channel B to channel B1, is unrestricted. Piston ③ is pushed by hydraulic oil pressure, which pushes the valve core ④ of check valve to produce displacement, so that hydraulic oil in channels A and A1 can flow in both directions, or hydraulic oil in channels B and B1 can flow in both directions.

[0003] In practical applications, stacked one-way throttle valves and stacked hydraulic locks are often used together to form a configuration such as... Figure 3 The hydraulic valve shown is made of Figure 3 It is evident that the valve composed of stacked one-way throttle valve and stacked hydraulic lock has a large volume, resulting in a long hydraulic oil circuit. This leads to a large pressure loss of hydraulic oil along the flow path and there are 8 potential points for external leakage. External leakage in hydraulic systems is usually a serious system problem. Summary of the Invention

[0004] This invention discloses a one-way throttling hydraulic lock and its working method, which solves the problem that the valve composed of a stacked one-way throttling valve and a stacked hydraulic lock has a large volume, resulting in a long hydraulic oil circuit, which leads to a large pressure loss of hydraulic oil along the path and many points where external leakage may occur. The invention integrates the functions of a hydraulic throttling valve and a hydraulic lock in the hydraulic field into one unit, which is small in size and avoids points where external leakage may occur.

[0005] To achieve the above objectives, the technical solution of the present invention is specifically implemented as follows:

[0006] The application discloses a one-way throttling hydraulic lock, which comprises a valve body, a valve cavity is formed in the valve body, a piston is slidably arranged in the valve cavity, the valve cavity is divided into a first cavity and a second cavity by the piston, the first cavity and the second cavity have the same internal structure, a first working oil channel, a second working oil channel, a third working oil channel and a fourth working oil channel are formed in the valve body, the first working oil channel and the second working oil channel are connected with the first cavity, and the third working oil channel and the fourth working oil channel are connected with the second cavity; a first connecting sleeve is arranged in the first cavity, the first connecting sleeve is coaxially arranged with the piston, a second connecting sleeve is connected with one end of the first connecting sleeve away from the piston, an adjusting rod is coaxially arranged in the first connecting sleeve and the second connecting sleeve, a conical valve sleeve is connected with one end of the adjusting rod towards the piston, a conical valve core and a spring are arranged in the conical valve sleeve, one end of the spring abuts against the adjusting rod, and the other end of the spring abuts against the conical valve core, the piston can contact the conical valve core and is pushed to slide under the pushing of hydraulic oil.

[0007] When the oil channel pressure of the third working oil channel reaches a certain proportion r of the oil channel pressure of the second working oil channel, and when the oil channel pressure of the first working oil channel reaches a certain proportion r of the oil channel pressure of the fourth working oil channel, the conical valve core is pushed by the piston, the flow area between the conical valve core and the conical valve sleeve is changed, and the hydraulic oil flow from the second working oil channel to the first working oil channel or the hydraulic oil flow from the fourth working oil channel to the third working oil channel is controlled.

[0008] Further, the piston is spindle-shaped.

[0009] Further, a plurality of oil grooves are formed in the end face of the first connecting sleeve towards the piston.

[0010] Further, the second connecting sleeve is threadedly connected with the first connecting sleeve.

[0011] Further, the adjusting rod is threadedly connected with the second connecting sleeve.

[0012] Further, one end of the adjusting rod towards the piston is connected with the conical valve sleeve through a spring pin.

[0013] Further, a limiting structure is formed in the end face of the first connecting sleeve towards the piston to limit the movement of the piston.

[0014] Further, sealing rings are arranged between the first connecting sleeve and the second connecting sleeve, between the adjusting rod and the second connecting sleeve, between the first connecting sleeve and the valve body, between the conical valve sleeve and the first connecting sleeve and between the piston and the valve body.

[0015] The application further discloses a working method of the one-way throttling hydraulic lock, which comprises the following working conditions:

[0016] In the initial state, the conical surface of the conical valve core in the valve body is pressed to the oil port of the conical valve sleeve, so that the hydraulic oil cannot flow from the second working oil passage to the first working oil passage regardless of whether the oil pressure of the second working oil passage oil port is greater than the oil pressure of the first working oil passage oil port, and the hydraulic oil cannot flow from the fourth working oil passage to the third working oil passage regardless of whether the oil pressure of the fourth working oil passage oil port is greater than the oil pressure of the third working oil passage oil port;

[0017] When the oil pressure of the first working oil passage oil port is greater than the oil pressure of the second working oil passage oil port, the hydraulic oil flows from the first working oil passage to the second working oil passage; when the oil pressure of the third working oil passage oil port is greater than the oil pressure of the fourth working oil passage oil port, the hydraulic oil flows from the third working oil passage to the fourth working oil passage;

[0018] When the oil passage pressure of the third working oil passage reaches a certain proportion r of the oil passage pressure of the second working oil passage, the conical valve core is pushed by the piston to form a certain flow area between the conical valve core and the conical valve sleeve, so that the hydraulic oil of the second working oil passage flows to the first working oil passage; when the oil passage pressure of the first working oil passage reaches a certain proportion r of the oil passage pressure of the fourth working oil passage, the conical valve core is pushed by the piston 13 to form a certain flow area between the conical valve core and the conical valve sleeve, so that the hydraulic oil of the fourth working oil passage flows to the third working oil passage.

[0019] Further, when the oil passage pressure of the third working oil passage reaches a certain proportion r of the oil passage pressure of the second working oil passage, and when the oil passage pressure of the first working oil passage reaches a certain proportion r of the oil passage pressure of the fourth working oil passage, the expression of the proportion r is:

[0020]

[0021] wherein,

[0022] d1 is the diameter of the piston;

[0023] d2 is the diameter of the axial oil port of the conical valve sleeve;

[0024] The expression of the flow area A formed between the conical valve core (145) and the conical valve sleeve (144) is:

[0025]

[0026] wherein,

[0027] θ is the half-conical angle of the conical valve core;

[0028] X1 is the distance between the end surface of the first connecting sleeve facing the piston and the piston when the conical valve core does not produce displacement;

[0029] x - distance between the cone valve sleeve and the first connecting sleeve.

[0030] Beneficial technical effects:

[0031] 1. The application discloses a one-way throttling hydraulic lock, which comprises a valve body, a valve cavity is formed in the valve body, a piston is slidably arranged in the valve cavity, the valve cavity is divided into a first cavity and a second cavity by the piston, the first cavity and the second cavity have the same internal structure, a first working oil channel, a second working oil channel, a third working oil channel and a fourth working oil channel are formed in the valve body, the first working oil channel and the second working oil channel are connected with the first cavity, and the third working oil channel and the fourth working oil channel are connected with the second cavity; a first connecting sleeve is installed in the first cavity, the first connecting sleeve is coaxially installed with the piston, a second connecting sleeve is connected to one end of the first connecting sleeve away from the piston, an adjusting rod is coaxially installed in the first connecting sleeve and the second connecting sleeve, a cone valve sleeve is connected to one end of the adjusting rod towards the piston, a cone valve core and a spring are arranged in the cone valve sleeve, one end of the spring abuts against the adjusting rod, and the other end of the spring abuts against the cone valve core, the piston can contact the cone valve core and is pushed to slide the cone valve core under the push of hydraulic oil, the functions of a hydraulic throttling valve and a hydraulic lock in the hydraulic field are integrated, the volume is small, and the point that may cause external leakage is avoided.

[0032] 2. In the application, a limiting structure is formed on the end face of the first connecting sleeve towards the piston, so that the movement of the piston is limited, and the piston can only move within a certain range.

[0033] 3. In the application, a sealing ring is arranged between the first connecting sleeve and the second connecting sleeve, a sealing ring is arranged between the adjusting rod and the second connecting sleeve, a sealing ring is arranged between the first connecting sleeve and the valve body, a sealing ring is arranged between the cone valve sleeve and the first connecting sleeve, and a sealing ring is arranged between the piston and the valve body, so that the valve body has good sealing performance and the friction between the parts is reduced.

[0034] 4. In the application, the rotatable adjusting rod is dragged to produce linear motion, thereby dragging the cone valve sleeve to produce displacement, and then the piston pushes the cone valve core to produce displacement, so as to change the flow area between the cone valve core and the cone valve sleeve, control the hydraulic oil flow from the second working oil channel to the first working oil channel or the hydraulic oil flow from the fourth working oil channel to the third working oil channel, and achieve the purpose of throttling. BRIEF DESCRIPTION OF DRAWINGS

[0035] In order to more clearly illustrate the technical solutions of the application, the following will briefly introduce the drawings needed to be used in the embodiment description.

[0036] Figure 1 Figure 1 is a schematic diagram of a prior art superimposed one-way throttle valve structure;

[0037] Figure 2 Figure 2 is a schematic diagram of a prior art superimposed hydraulic lock structure;

[0038] Figure 3 Figure 3 is a schematic diagram of a prior art valve structure composed of superimposed one-way throttle valve and superimposed hydraulic lock;

[0039] Figure 4 Figure 4 is a schematic diagram of a one-way throttle hydraulic lock according to the present application;

[0040] Figure 5 Figure 5 is a force diagram of the conical valve core and the piston in the one-way throttle hydraulic lock according to the present application.

[0041] Wherein, 1-valve body, 12-valve cavity, 13-piston, 14-first cavity, 15-second cavity, 16-first working oil way, 17-second working oil way, 18-third working oil way, 19-fourth working oil way, 141-first connecting sleeve, 142-second connecting sleeve, 143-adjusting rod, 144-conical valve sleeve, 145-conical valve core, 146-spring, 1411-limiting structure. DETAILED DESCRIPTION

[0042] Embodiments of the present application are described in detail below with reference to the attached drawing figures, wherein the same or like reference numerals and letters in the drawing figures and the following description denote the same or like elements or components. The embodiments described below are merely exemplary for the purpose of explanation and are not intended to limit the present application.

[0043] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments consistent with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0044] The foregoing is considered as illustrative only of the principles of the application. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the application to the exact construction and practice described. Accordingly, all such variations are intended to be included within the scope of the present application as defined in the following claims, along with full equivalents thereof.

[0045] In the description of the present application, it is to be understood that the orientation terms such as "front", "back", "up", "down", "left", "right", "transverse", "vertical", "horizontal", "top", "bottom", etc. indicate the orientation or positional relationship shown in the drawings, which are merely for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore cannot be construed as limiting the scope of protection of the present application. The orientation terms "inner", "outer" refer to the inner and outer relative to the contour of the components themselves.

[0046] For the convenience of description, spatial relative terms such as "over", "above", "upper surface", "upper", etc. can be used herein to describe the spatial positional relationship of one device or feature with respect to other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the devices described in the drawings. For example, if the devices in the drawings are inverted, the device described as "above" or "over" other devices or structures will be positioned "below" or "under" the other devices or structures. Thus, the exemplary term "above" can include both "above" and "below" orientations. The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein are interpreted accordingly.

[0047] In addition, it should be noted that the use of the terms "first", "second", etc. to describe components is merely for the convenience of distinguishing the corresponding components, and the above terms do not have special meanings unless otherwise stated, and therefore cannot be construed as limiting the scope of protection of the present application.

[0048] The embodiments of the present application will be described in detail below with reference to the drawings.

[0049] To solve the problem of large volume of the valve composed of the superimposed one-way throttle valve and the superimposed hydraulic lock in the prior art, which leads to long hydraulic oil path and large pressure loss of the hydraulic oil along the path, and many points where external leakage is likely to occur, the present application discloses an integrated one-way throttle hydraulic lock.

[0050] The one-way throttle hydraulic lock disclosed by the present application is shown in Figure 4 , and specifically comprises a valve body 1, the valve body 1 has a valve cavity formed inside, a piston 13 is slidably arranged in the valve cavity, preferably, the piston 13 is spindle-shaped as a whole, and the two side terminals of the piston 13 can contact a spool valve core 145, which can be pushed to slide by the hydraulic oil, the valve cavity is divided into a first cavity 14 and a second cavity 15 by the piston 13, and the internal structures of the first cavity 14 and the second cavity 15 are the same (i.e. the valve body 1 is symmetrical relative to the central axis of the piston 13 when the piston 13 is in the middle position of the valve cavity 12), the valve body 1 has a first working oil channel 16, a second working oil channel 17, a third working oil channel 18 and a fourth working oil channel 19 formed inside, the first working oil channel 16 and the second working oil channel 17 are connected to the first cavity 14, and the third working oil channel 18 and the fourth working oil channel 19 are connected to the second cavity 15; a first connecting sleeve 141 is installed in the first cavity 14, the first connecting sleeve 141 is coaxially installed with the piston 13, a plurality of oil grooves are formed on the end face of the first connecting sleeve 141 facing the piston 13, a second connecting sleeve 142 is connected to the end of the first connecting sleeve 141 away from the piston 13, preferably, the second connecting sleeve 142 is connected to the first connecting sleeve 141 by screwing, an adjusting rod 143 is coaxially installed inside the first connecting sleeve 141 and the second connecting sleeve 142, preferably, the adjusting rod 143 is connected to the second connecting sleeve 142 by screwing, a spool sleeve 144 is connected to the end of the adjusting rod 143 facing the piston 13, preferably, the end of the adjusting rod 143 facing the piston 13 is connected to the spool sleeve 144 by a spring pin, a spool valve core 145 and a spring 146 are arranged inside the spool sleeve 144, one end of the spring 146 abuts against the adjusting rod 143, and the other end abuts against the spool valve core 145, to help reset the spool valve core 145, the adjusting rod 143 realizes linear motion by screwing with the second connecting sleeve 142, thereby dragging the spool sleeve 144 to realize linear motion, so as to adjust the position of the spool sleeve 144.

[0051] When the oil passage pressure of the third working oil passage 18 reaches a certain proportion r of the oil passage pressure of the second working oil passage 17, and when the oil passage pressure of the first working oil passage 16 reaches a certain proportion r of the oil passage pressure of the fourth working oil passage 19, the conical valve core 145 is pushed by the piston 13 to control the hydraulic oil flow from the second working oil passage 17 to the first working oil passage 16 or the hydraulic oil flow from the fourth working oil passage 19 to the third working oil passage 18 by changing the flow area between the conical valve core 145 and the conical valve sleeve 144.

[0052] As a preferred embodiment of the present application, a limiting structure 1411 is formed on the end face of the first connecting sleeve 141 towards the piston 13 to limit the movement of the piston 13.

[0053] As a preferred embodiment of the present application, a sealing ring is arranged between the first connecting sleeve 141 and the second connecting sleeve 142, a sealing ring is arranged between the adjusting rod 143 and the second connecting sleeve 142, and a sealing ring is arranged between the first connecting sleeve 141 and the valve body 1, between the conical valve sleeve 144 and the first connecting sleeve 141, and between the piston 13 and the valve body 1, which not only ensures the overall sealing property of the valve body 1, but also effectively reduces the friction between the parts and prolongs the service life of the parts.

[0054] The present application further discloses a working method of the one-way throttling hydraulic lock, which includes the following working conditions:

[0055] In the initial state, the conical surface of the conical valve core 145 in the valve body 1 is pressed onto the oil port of the conical valve sleeve 144, which makes the hydraulic oil unable to flow from the second working oil passage 17 to the first working oil passage 16 regardless of whether the oil pressure P a1 of the second working oil passage 17 is greater than the oil pressure P a of the first working oil passage 16, and the hydraulic oil unable to flow from the fourth working oil passage 19 to the third working oil passage 18 regardless of whether the oil pressure P b of the fourth working oil passage 19 is greater than the oil pressure P a of the third working oil passage 18.

[0056] When the oil pressure P a1 of the second working oil passage 17 is greater than the oil pressure P a of the first working oil passage 16, the hydraulic oil flows from the first working oil passage 16 to the second working oil passage 17; and when the oil pressure P b of the third working oil passage 18 is greater than the oil pressure P b of the fourth working oil passage 19, the hydraulic oil flows from the third working oil passage 18 to the fourth working oil passage 19.

[0057] When the oil passage pressure P b of the third working oil passage 18 reaches the oil passage pressure P a1When the pressure is at a certain ratio r, the cone valve core 145 is pushed by the piston 13 (moving towards the first cavity to the limiting structure 1411 of the first connecting sleeve 141), causing the cone valve core 145 to move away from the oil port of the cone valve sleeve 144, forming a certain flow area between the cone valve core 145 and the cone valve sleeve 144, allowing the hydraulic oil in the second working oil passage 17 to flow to the first working oil passage 16; when the oil passage pressure P in the first working oil passage 16... a When the oil pressure in the fourth working oil passage 19 reaches a certain proportion r, the cone valve core 145 will be pushed by the piston 13 (moving towards the second cavity to the limiting structure 1411 of the first connecting sleeve 141), so that the cone valve core 145 moves away from the oil port of the cone valve sleeve 144, and a certain flow area is formed between the cone valve core 145 and the cone valve sleeve 144, so that the hydraulic oil in the fourth working oil passage 19 flows to the third working oil passage 18.

[0058] See Figure 5 The force diagram of the cone valve core 145 and piston 13. Ignoring friction and damping forces, the force equation for the cone valve core 145 when it is open is:

[0059]

[0060] in,

[0061] d1 — Piston diameter;

[0062] d2—Axial oil port diameter of the cone valve sleeve;

[0063] P a —Pressure of the first working oil passage;

[0064] P a1 —Pressure of the second working oil passage;

[0065] P b —Pressure of the third working oil passage;

[0066] F s —The compressive force of a spring.

[0067] In practical applications, the pressure P of the first working oil passage a The force is so low as to be negligible (zero). Spring 146 in this valve only serves to reset the cone valve core 145, and its spring force F... s It is very small and can be ignored as zero in Equation 1. The above equation can be rearranged as:

[0068]

[0069] The critical adjustment at which the valve core opens is obtained is:

[0070]

[0071] The calculation formula of the flow area A between the spool 145 and the spool sleeve 144 is as follows:

[0072]

[0073] Wherein,

[0074] θ - the half-cone angle of the spool;

[0075] X1 - the distance between the end surface of the first connecting sleeve facing the piston and the piston when the spool has no displacement;

[0076] x - the distance between the spool sleeve and the first connecting sleeve.

[0077] In the calculation formula of the flow area A between the spool 145 and the spool sleeve 144, only the distance x between the end surface of the spool sleeve 144 and the first connecting sleeve 141 is a variable. When the spool sleeve 144 is axially displaced by dragging the rotary adjusting rod 143, x becomes larger or smaller.

[0078] When x is 0, the second term in the calculation formula of the flow area A between the spool 145 and the spool sleeve 144 reaches the minimum value, and the flow area A between the spool 145 and the spool sleeve 144 reaches the maximum value:

[0079]

[0080] When x≥X1, the second term in the calculation formula of the flow area A between the spool 145 and the spool sleeve 144 reaches the maximum value, and the flow area A between the spool 145 and the spool sleeve 144 = 0.

[0081] Therefore, it can be seen that the one-way throttling hydraulic lock disclosed in the present application changes the flow area between the spool 145 and the spool sleeve 144 by rotating the adjusting rod 143 to make it produce linear motion, dragging the spool sleeve 144 to produce displacement, and then the piston pushes the spool to produce displacement, thereby controlling the hydraulic oil flow from the second working oil passage 17 to the first working oil passage 16 or the hydraulic oil flow from the fourth working oil passage 19 to the third working oil passage 18.

[0082] Briefly, the flow area A between the conical valve spool 145 and the conical valve sleeve 144 is related to the relative displacement X between the conical valve sleeve 144 and the first connecting sleeve 141, so that the rotary adjusting rod 143 can be rotated to produce linear motion, thereby dragging the conical valve sleeve 144 to produce displacement, and then the piston 13 pushes the conical valve spool 145 to produce displacement, so as to change the flow area between the conical valve spool 145 and the conical valve sleeve 144 (the position of the conical valve sleeve 144 is different, the distance between the conical valve spool 145 and the conical valve sleeve 144 is different, so that the opening size between the conical valve spool 145 and the conical valve sleeve 144 is different, and thus the flow area between the conical valve spool 145 and the conical valve sleeve 144 is different), thereby controlling the hydraulic oil flow from the second working oil passage 17 to the first working oil passage 16 or the hydraulic oil flow from the fourth working oil passage 19 to the third working oil passage 18.

[0083] In the description of the present specification, the description of the terms "one embodiment", "some embodiments", "an example", "a specific example", or "some examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0084] The above embodiments only describe the preferred embodiments of the present application, and do not limit the scope of the present application. Without departing from the design spirit of the present application, various modifications and improvements of the technical solutions of the present application made by those skilled in the art shall fall within the protection scope determined by the claims of the present application.

Claims

1. A one-way throttling hydraulic lock characterized in that, The valve body (1) is internally formed with a valve cavity, a piston (13) is slidably arranged in the valve cavity, the valve cavity is divided into a first cavity (14) and a second cavity (15) by the piston (13), the first cavity (14) and the second cavity (15) have the same internal structure, the valve body (1) is internally formed with a first working oil passage (16), a second working oil passage (17), a third working oil passage (18) and a fourth working oil passage (19), the first working oil passage (16) and the second working oil passage (17) are connected with the first cavity (14), and the third working oil passage (18) and the fourth working oil passage (19) are connected with the second cavity (15); a first connecting sleeve (141) is arranged in the first cavity (14), the first connecting sleeve (141) is coaxially arranged with the piston (13), one end of the first connecting sleeve (141) away from the piston (13) is connected with a second connecting sleeve (142), the first connecting sleeve (141) and the second connecting sleeve (142) are coaxially arranged with an adjusting rod (143) arranged inside, one end of the adjusting rod (143) towards the piston (13) is connected with a conical valve sleeve (144), the conical valve sleeve (144) is internally arranged with a conical valve core (145) and a spring (146), one end of the spring (146) abuts against the adjusting rod (143), and the other end of the spring (146) abuts against the conical valve core (145), the piston (13) can contact the conical valve core (145) and push the conical valve core (145) to slide under the push of hydraulic oil; When the oil passage pressure of the third working oil passage (18) reaches a certain proportion r of the oil passage pressure of the second working oil passage (17), and when the oil passage pressure of the first working oil passage (16) reaches a certain proportion r of the oil passage pressure of the fourth working oil passage (19), the conical valve core (145) is pushed by the piston (13), the flow area between the conical valve core (145) and the conical valve sleeve (144) is changed, and the hydraulic oil flow from the second working oil passage (17) to the first working oil passage (16) or the hydraulic oil flow from the fourth working oil passage (19) to the third working oil passage (18) is controlled.

2. A one-way throttling hydraulic lock according to claim 1, characterized in that The piston (13) is spindle-shaped.

3. A one-way throttling hydraulic lock according to claim 1, wherein A plurality of oil grooves are formed in the end face of the first connecting sleeve (141) towards the piston (13).

4. A one-way throttling hydraulic lock according to claim 1, wherein The second connecting sleeve (142) is threadedly connected with the first connecting sleeve (141).

5. A one-way throttling hydraulic lock according to claim 1, wherein The adjusting rod (143) is threadedly connected with the second connecting sleeve (142).

6. A one-way throttling hydraulic lock according to claim 1, wherein One end of the adjusting rod (143) towards the piston (13) is connected with the conical valve sleeve (144) through a spring pin.

7. A one-way throttling hydraulic lock according to claim 1, wherein A limiting structure (1411) is formed in the end face of the first connecting sleeve (141) towards the piston (13) to limit the movement of the piston (13).

8. A one-way throttling hydraulic lock according to claim 1, wherein The first connecting sleeve (141) and the second connecting sleeve (142) are provided with a sealing ring; the adjusting rod (143) and the second connecting sleeve (142) are provided with a sealing ring; the first connecting sleeve (141) and the valve body (1), the cone valve sleeve (144) and the first connecting sleeve (141), and the piston (13) and the valve body (1) are all provided with a sealing ring.

9. A method of operating a one-way throttling hydraulic lock as claimed in any one of claims 1 to 8, characterized in that, The working conditions include the following conditions: In the initial state, the conical surface of the conical valve core (145) in the valve body (1) is pressed onto the oil port of the conical valve sleeve (144), which makes the hydraulic oil unable to flow from the second working oil passage (17) to the first working oil passage (16) regardless of whether the oil pressure of the oil port of the second working oil passage (17) is greater than that of the oil port of the first working oil passage (16); the hydraulic oil cannot flow from the fourth working oil passage (19) to the third working oil passage (18) regardless of whether the oil pressure of the oil port of the fourth working oil passage (19) is greater than that of the oil port of the third working oil passage (18); When the oil pressure of the oil port of the first working oil passage (16) is greater than that of the oil port of the second working oil passage (17), the hydraulic oil flows from the first working oil passage (16) to the second working oil passage (17); when the oil pressure of the oil port of the third working oil passage (18) is greater than that of the oil port of the fourth working oil passage (19), the hydraulic oil flows from the third working oil passage (18) to the fourth working oil passage (19); When the oil passage pressure of the third working oil passage (18) reaches a certain proportion r of the oil passage pressure of the second working oil passage (17), the conical valve core (145) is pushed by the piston (13) to form a certain flow area between the conical valve core (145) and the conical valve sleeve (144), so that the hydraulic oil of the second working oil passage (17) flows to the first working oil passage (16); when the oil passage pressure of the first working oil passage (16) reaches a certain proportion r of the oil passage pressure of the fourth working oil passage (19), the conical valve core (145) is pushed by the piston (13) to form a certain flow area between the conical valve core (145) and the conical valve sleeve (144), so that the hydraulic oil of the fourth working oil passage (19) flows to the third working oil passage (18). When the oil passage pressure of the third working oil passage (18) reaches a certain proportion r of the oil passage pressure of the second working oil passage (17), and the oil passage pressure of the first working oil passage (16) reaches a certain proportion r of the oil passage pressure of the fourth working oil passage (19), the expression of the proportion r is:

10. A method of operating a one-way throttling hydraulic lock as defined in claim 9, wherein, wherein, d1 is the diameter of the piston; d2 is the diameter of the axial oil port of the conical valve sleeve; The expression of the flow area A formed between the conical valve core (145) and the conical valve sleeve (144) is: wherein, θ is the half-cone angle of the conical valve core; X1 is the distance between the end surface of the first connecting sleeve facing the piston and the piston when the conical valve core has no displacement; x is the distance between the conical valve sleeve and the first connecting sleeve. ​

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