Valve assembly with optimized linearity and servo valve

Abstract

The utility model provides a valve assembly with optimized linearity and a servo valve, and relates to the technical field of servo valve manufacturing, the valve assembly comprises a valve sleeve, a valve core arranged in the valve sleeve, a crankshaft connected with the valve core and used for driving the valve core to move in the valve sleeve, and a motor rotor connected with the crankshaft; the crankshaft is of an eccentric structure, a plurality of sets of through holes are formed in the valve sleeve in the axial direction, steps are arranged on the valve element and can shield the through holes, the unshielded area is a throttling window, and the area of the throttling window can be adjusted by moving the valve element. The shape of the through hole is used for nonlinear compensation of a motor rotation angle and a throttling window area, so that the motor rotor angle and the throttling window area are in a linear change relation.

Description

Technical Field

[0001] This utility model relates to the field of servo valve manufacturing technology, and in particular to a valve assembly and servo valve with optimized linearity. Background Technology

[0002] Servo valves are precision control components in hydraulic systems that control the flow and direction of the working fluid. Flow control is achieved by adjusting the size of the window formed by the edge of the orifice on the valve sleeve or integrated valve body and the shoulder of the valve core step.

[0003] Currently, a transmission method where a rotary motor drives a motor rotor to rotate at a certain angle, and then the valve core moves linearly through the interaction between the motor rotor crankshaft and the valve core, is widely used. The control signal and the motor rotor rotation angle have a linear relationship; however, the relationship between the motor rotor rotation angle and the valve core movement distance is non-linear. Traditional valve sleeves or integrated valve bodies have square orifice designs, so the valve core movement distance and the resulting flow window area are linear, while the relationship between the control signal and the flow window area is non-linear. Therefore, this transmission method leads to poor linearity of the servo valve flow-control signal curve; the closer the control signal is to the rated signal, the more curved the flow curve becomes.

[0004] Existing solutions to the above problems mainly focus on algorithms, processing the control algorithm for the motor rotation angle to make the control signal and the motor rotor rotation angle nonlinear, thereby compensating for the curvature of the flow curve. However, this solution is difficult to implement, has low precision in adjusting the motor rotor rotation angle, and due to the accumulation of machining errors in other components, each servo valve needs to be individually adjusted and calibrated after assembly to achieve flow curve compensation, consuming excessive manpower and resources. Utility Model Content

[0005] The main objective of this invention is to propose a valve assembly and servo valve with optimized linearity, aiming to optimize the linearity of the valve assembly.

[0006] To achieve the above objectives, this utility model proposes a valve assembly with optimized linearity, comprising a valve sleeve, a valve core disposed within the valve sleeve, a crankshaft connected to the valve core and used to drive the valve core to move within the valve sleeve, and a motor rotor connected to the crankshaft; the crankshaft has an eccentric structure, the valve sleeve has multiple sets of through holes along the axial direction, the valve core has steps that can block the through holes, and the unblocked area is a throttling window, the movement of the valve core can adjust the area of ​​the throttling window; the shape of the through holes is used for nonlinear compensation of the motor rotation angle and the throttling window area, so that the motor rotor angle and the throttling window area have a linear relationship.

[0007] Preferably, the length direction of the through hole is parallel to the axial direction of the valve core, and the shape of the through hole satisfies the following relationship:

[0008] ;

[0009] ;

[0010] Where: x is the distance between the edge of the step and the edge of the through hole; h is the height of the through hole when the distance between the edge of the through hole and the edge of the step is x; y is the area of ​​the throttling window when the distance between the edge of the through hole and the edge of the step is x; r is the eccentricity of the crankshaft; α is the rotation angle of the motor rotor; b, c, and n are constants related to the valve assembly design.

[0011] For through-hole shapes that satisfy the above relationships, the rotor angle of the motor and the area of ​​the throttling window change linearly.

[0012] Preferably, when the transmission relationship between the motor rotor and the valve core is a crankshaft-connecting rod type or a crankshaft-bore type, n is 0.

[0013] Preferably, when the transmission relationship between the motor rotor and the valve core is a crankshaft-deflection rod type, n is 1 / 2.

[0014] Preferably, the valve sleeve has A sets of through holes arranged axially, and each set of through holes includes B slots distributed radially along the valve sleeve; the value of A ranges from 1 to 16, the value of B ranges from 1 to 15, and the maximum size of the slot is 0.1 mm to 20 mm.

[0015] Preferably, when B is greater than 1: y represents the sum of the throttling window areas of the B slots, and h represents the sum of the height values ​​of the B slots when the distance from the edge of the through hole to the edge of the step is x.

[0016] Preferably, when B is greater than 1: among the B slots in each group of through holes, there are Bx regular holes and By irregular holes, and the number of Bx is greater than or equal to 0;

[0017] A regular hole is a slot whose height is a fixed value when the distance between the edge of the slot and the edge of the step is any value; slots other than regular holes are irregular holes.

[0018] y represents the sum of the throttling window areas of Bx regular holes and By irregular holes, and h represents the sum of the heights of Bx regular holes and By irregular holes when the distance from the edge of the through hole to the edge of the step is x.

[0019] Preferably, the shape of the through hole is one or more of the following: circular, elliptical, square with rounded corners, square with chamfered corners, square with conic curve transition, and square with polynomial curve transition.

[0020] Preferably, the rounding diameter of the square right-angled rounded corner is 0.05 mm to 9.5 mm.

[0021] This utility model also provides a servo valve, including the valve assembly as described above.

[0022] The technical solution of this utility model compensates for the nonlinear relationship between the motor rotation angle and the throttling window area by using the shape of the through hole, so that the motor rotor angle and the throttling window area have a linear relationship. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0024] Figure 1 A schematic diagram of the crankshaft-deflection rod transmission relationship of a linearity-optimized valve assembly provided by this utility model;

[0025] Figure 2 for Figure 1 A magnified view of a section at point A in the middle;

[0026] Figure 3 A schematic diagram of the crankshaft-orifice transmission relationship of a valve assembly with optimized linearity provided by this utility model;

[0027] Figure 4 for Figure 3 A magnified view of a section at point B in the middle;

[0028] Figure 5 A schematic diagram of a valve body with a valve sleeve for a linearity-optimized valve assembly provided by this utility model;

[0029] Figure 6 A schematic diagram of an integrated valve body for a linearity-optimized valve assembly provided by this utility model;

[0030] Figure 7 A flowchart illustrating a design method for a valve assembly with optimized linearity provided by this utility model.

[0031] Explanation of icon numbers:

[0032] Valve sleeve 10, valve core 11, crankshaft 12, motor rotor 13, through hole 14, slot 141, step 21, throttling window 22, valve body 24.

[0033] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0034] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0035] It should be noted that if any directional indication (such as up, down, left, right, front, back, etc.) is involved in the embodiments of this utility model, such directional indication is only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indication will also change accordingly. Unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal connection of two components. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0036] Furthermore, if the embodiments of this utility model involve descriptions such as "first," "second," etc., such descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Moreover, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0037] Servo valves are precision control components in hydraulic systems that can control the flow and direction of the working fluid. Flow control is achieved by the size of the window formed by the edge of the hole on the valve sleeve 10 or integrated valve body 24 and the shoulder of the step 21 on the valve core 11.

[0038] Currently, a transmission method widely used involves a rotary motor driving a motor rotor 13 to rotate at a certain angle, which in turn drives the valve core 11 to move linearly through the interaction between the motor rotor 13 crankshaft 12 and the valve core 11. The control signal and the rotation angle of the motor rotor 13 have a linear relationship; however, the relationship between the rotation angle of the motor rotor 13 and the movement distance of the valve core 11 is non-linear. Traditional valve sleeve 10 or integrated valve body 24 has a square hole design, so the movement distance of the valve core 11 and the area of ​​the final flow window are linear, resulting in a non-linear relationship between the control signal and the flow window area. Therefore, this transmission method leads to poor linearity of the servo valve flow-control signal curve; the closer the control signal is to the rated signal, the more curved the flow curve becomes. Existing technologies primarily address this problem through algorithmic processing, modifying the control algorithm for the motor rotation angle to make the relationship between the control signal and the rotation angle of the motor rotor 13 non-linear, thereby compensating for the curvature of the flow curve. However, the implementation of this solution is difficult. The rotation angle accuracy of the motor rotor 13 is low. Furthermore, due to the accumulation of machining errors in other components, each servo valve needs to be individually debugged and its parameters calibrated after assembly to achieve flow curve compensation, which consumes too much manpower and resources.

[0039] This invention proposes a valve assembly with optimized linearity, aiming to improve the linearity of the valve assembly.

[0040] In one embodiment of this utility model, a valve assembly with optimized linearity is proposed, including a valve sleeve 10, a valve core 11 disposed within the valve sleeve 10, a crankshaft 12 connected to the valve core 11 and used to drive the valve core 11 to move within the valve sleeve 10, and a motor rotor 13 connected to the crankshaft 12; the crankshaft 12 has an eccentric structure, and the valve sleeve 10 has multiple sets of through holes 14 along the axial direction. The valve core 11 has a step 21, which can block the through holes 14. The unblocked area is a throttling window 22, and the movement of the valve core 11 can adjust the area of ​​the throttling window 22; the shape of the through holes 14 is used for nonlinear compensation of the motor rotation angle and the area of ​​the throttling window 22, so that the angle of the motor rotor 13 and the area of ​​the throttling window 22 have a linear relationship.

[0041] Servo valves control the flow rate and direction of the working fluid via control signals. By inputting precise control signals, which can be current or voltage values, the servo valve controls the flow rate and direction of the working fluid accordingly. The closer the linear relationship between the control signal and the flow rate value, the higher the accuracy.

[0042] In most servo valves, the crankshaft 12 is driven to rotate by an electric motor, which in turn drives the valve core 11 to move. Since the rotation generates two vertical components, one of which is used to drive the valve core 11 to move, this transmission method results in poor linearity between the servo valve flow rate and the control signal curve. The closer the control signal is to the rated signal, the more curved the flow rate curve becomes.

[0043] In this embodiment, the displacement component generated by the rotation of the crankshaft 12 is compensated by changing the opening degree of the through hole 14 on the valve sleeve 10, so that the control signal and the flow rate value are approximately linearly related. The opening degree of the through hole 14 refers to the change in the area of ​​the throttling window 22 corresponding to the movement distance of the valve core 11.

[0044] Specifically, such as Figure 2 , Figure 4 As shown, the rotation of crankshaft 12 generates X and Y components, and the valve core 11 is axially parallel to the X direction. When the X-direction displacement component of crankshaft 12 increases, a certain angle of crankshaft 12 rotation results in an increasing displacement of valve core 11; the opening of the corresponding position of through hole 14 decreases, meaning the step 21 on valve core 11 moves within this range, and the increase in the area of ​​throttling window 22 decreases. Conversely, when the X-direction displacement component of crankshaft 12 decreases, a certain angle of crankshaft 12 rotation results in a decreasing displacement of valve core 11; the opening of the corresponding position of through hole 14 increases, meaning the step 21 on valve core 11 moves within this range, and the increase in the area of ​​throttling window 22 increases. Ultimately, the relationship between the crankshaft 12 rotation angle and the change in the area of ​​throttling window 22 tends to be linear.

[0045] Furthermore, the length direction of the through hole 14 is parallel to the axial direction of the valve core 11, and the shape of the through hole 14 satisfies the following relationship:

[0046] ;

[0047] ;

[0048] Where: x is the distance between the edge of step 21 and the edge of through hole 14; h is the height of through hole 14 when the distance between the edge of through hole 14 and the edge of step 21 is x; y is the area of ​​throttling window 22 when the distance between the edge of through hole 14 and the edge of step 21 is x; r is the eccentricity of crankshaft 12; α is the rotation angle of motor rotor 13; b, c, and n are constants related to valve assembly design.

[0049] The shape of the through hole 14 satisfies the above relationship, and the angle of the motor rotor 13 and the area of ​​the throttling window 22 have a linear relationship.

[0050] This embodiment proposes a functional relationship that defines the shape of the through hole 14. x is the distance between the edge of the step 21 and the edge of the through hole 14. Since the step 21 has a width, x is the distance between the edge of the step 21 near the throttling window 22 and the edge of the through hole 14.

[0051] In this embodiment, when the transmission relationship between the motor rotor 13 and the valve core 11 is crankshaft 12-connecting rod type or crankshaft 12-hole type, n is 0. Figure 3 as well as Figure 4A schematic diagram of the crankshaft 12-hole transmission relationship is shown. The crankshaft 12 is connected to the motor rotor. The valve core 11 is provided with a waist-shaped connecting hole. One end of the crankshaft 12 is inserted into the waist-shaped connecting hole. The length direction of the waist-shaped connecting hole is parallel to the Y direction. When the crankshaft 12 rotates, the X-direction component is manifested in the movement of the valve core 11, and the Y-direction component is manifested in the movement of the crankshaft 12 in the waist-shaped connecting hole.

[0052] In this embodiment, when the transmission relationship between the motor rotor 13 and the valve core 11 is crankshaft 12-deflection rod type, n is 1 / 2.

[0053] In this embodiment, Figure 1 , Figure 2 The diagram shows the transmission relationship of crankshaft 12-deflection rod type. The X-direction component is manifested in the movement of valve core 11, and the Y-direction component is manifested in the change of deflection rod angle.

[0054] Furthermore, the valve sleeve 10 is axially arranged with a group of through holes 14, each group of through holes 14 including B slots 141 distributed radially along the valve sleeve 10; the value of A ranges from 1 to 16, the value of B ranges from 1 to 15, and the maximum size of the slot 141 is 0.1 mm to 20 mm.

[0055] In the specific implementation process, the servo valve also includes a valve body 24, which is provided with a flow channel system. The flow channel system includes multiple flow channel units, each of which is connected to different A group through holes 14. The motor drives the valve stem to rotate, and the crankshaft 12 drives the valve core 11 and the valve sleeve 10 to move axially relative to each other, thereby adjusting the direction of fluid flow in the flow channel system.

[0056] Step 21 is an annular part fixed on valve core 11. The outer circular surface of step 21 fits against the inner wall of valve sleeve 10, and fluid on both sides of step 21 cannot flow between them through the gap between step 21 and valve sleeve 10. The variable fluid space is the space surrounding the outside of valve core 11. The variable fluid space can be the space enclosed by the outer wall of valve core 11, the inner wall of valve sleeve 10, and two adjacent steps 21, or it can be the space enclosed by the outer wall of valve core 11, the inner wall of valve sleeve 10, the end of valve sleeve 10, and step 21.

[0057] Step 21 can completely or partially cover a set of through holes 14. When completely covered, the fluid in the flow channel system cannot flow into the variable fluid space corresponding to the set of through holes 14 through the set of through holes 14, and the fluid in the variable fluid space corresponding to the set of through holes 14 cannot flow into the flow channel system through the set of through holes 14.

[0058] When step 21 partially covers a set of through holes 14, the area of ​​these through holes 14 that allows fluid to pass through is the window area. The movement of valve core 11 can also adjust the size of the window area, thereby controlling the flow rate of fluid passing through the window.

[0059] Each flow channel unit can be a single channel, or a channel consisting of a main flow channel and multiple branch flow channels. One end of each branch flow channel is connected to a slot 141.

[0060] Furthermore, when B is greater than 1: y represents the sum of the areas of the throttling windows 22 of the B slots 141, and h represents the sum of the heights of the B slots 141 when the distance from the edge of the through hole 14 to the edge of the step 21 is x.

[0061] When the number of slots 141 is greater than 1: multiple slots 141 serve to divide and merge the flow, and the throttling window 22 is composed of the windows on these slots 141. Therefore, y represents the sum of the areas of the throttling windows 22 of B slots 141, and h represents the sum of the heights of B slots 141 when the distance from the edge of the through hole 14 to the edge of the step 21 is x.

[0062] Furthermore, when B is greater than 1: among the B slots 141 of each group of through holes 14, there are Bx regular holes and By irregular holes, and the number of Bx is greater than or equal to 0;

[0063] A regular hole is a slot 141 whose height is a fixed value when the distance between the edge of the slot 141 and the edge of the step 21 is any value; slots 141 other than regular holes are irregular holes.

[0064] y represents the sum of the areas of the throttling windows 22 of Bx regular holes and By irregular holes, and h represents the sum of the heights of Bx regular holes and By irregular holes when the distance from the edge of the through hole 14 to the edge of the step 21 is x.

[0065] In this embodiment, the B slots 141 in each group of through holes 14 can be composed entirely of irregular holes, or they can be composed of regular holes and irregular holes. Regular holes are slots 141 that do not perform flow compensation, while irregular holes are slots 141 with flow compensation function obtained according to the aforementioned calculation method.

[0066] Furthermore, the shape of the through hole 14 is one or more of the following: circular, elliptical, square with rounded corners, square with chamfered corners, square with conic curve transition, and square with polynomial curve transition.

[0067] Furthermore, the rounding diameter of the square right-angled rounded corner is 0.05 mm to 9.5 mm.

[0068] In some embodiments, such as Figure 5 As shown, valve sleeve 10 and valve body 24 can be two parts, which are processed separately and then assembled.

[0069] In some embodiments, such as Figure 6As shown, the valve sleeve 10 and the valve body 24 can be integrally formed, and the valve sleeve 10 is a part of the valve body 24.

[0070] In some embodiments, for the crankshaft 12-deflection rod type fit, the rotating shaft of the motor rotor 13 is designed to be coaxial with the center line of the end hole of the deflection rod of the valve core 11. The eccentricity of the motor rotor 13 to the crankshaft 12 is 1.5 mm (r), the length of the deflection rod of the valve core 11 is 90 mm (l), and the rotation angle of the motor rotor 13 is α. The angle of the motor rotor 13 when the deflection rod of the valve core 11 coincides with the moving shaft of the valve core 11 is set to 0°, and α rotates within the range of -50° to +50°. At this time, the expression for the distance x that the valve core 11 moves is:

[0071] ;

[0072] Substituting the data, the expression is:

[0073] ;

[0074] If the height of the flow window at position x is h, then the area of ​​the flow window y is:

[0075] ;

[0076] In the above formula, x is the distance between the edge of step 21 and the edge of through hole 14; h is the height of through hole 14 when the distance between the edge of through hole 14 and the edge of step 21 is x; y is the area of ​​throttling window 22 when the distance between the edge of through hole 14 and the edge of step 21 is x; r is the eccentricity of crankshaft 12; α is the rotation angle of motor rotor 13; b, c, and n are constants related to valve assembly design.

[0077] In the above formula, y is the area of ​​the throttling window 22 at position x, and α is the rotation angle of the motor rotor 13. We need y and α to have a linear relationship, so we set a linear coefficient m to solve for the relationship between h and x, and h and α.

[0078] Based on h(x), the height of the hole corresponding to different valve core 11 positions (x) can be obtained.

[0079] In some embodiments, the explicit analytical solution of the h(x) function can be obtained directly, and the shape of the slot or through hole can be designed based on the function.

[0080] In some embodiments, an explicit analytical solution to the function h(x) cannot be obtained. In such cases, an iterative method can be used to solve for h for specific x and m. Alternatively, the correspondence between h(x) values ​​can be pre-calculated to design the shape of slots or through holes.

[0081] This utility model also provides a servo valve, including the valve assembly as described above.

[0082] like Figure 7 As shown, the shape curve expression of the orifice of valve sleeve 10 or integrated valve body 24 is calculated according to the following design method: S1, Obtain the three-dimensional model of the servo valve including the flow channel, valve sleeve 10, valve core 11, and motor rotor 13, and calculate the nonlinear relationship of the motor rotor 13 driving the valve core 11; S2, Calculate the input control signal-window area relationship from the relationship between motor rotation angle and valve core 11 movement distance; S3, Require the window area and input control signal relationship to be linear, and calculate the orifice height of valve sleeve 10 under different valve core 11 positions; S4, Design the orifice shape according to the orifice height of valve sleeve 10 under different valve core 11 positions to obtain a flow-control signal curve with improved linearity.

[0083] In various embodiments of this utility model, it should be understood that the sequence number of each process does not necessarily imply the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of this utility model embodiment.

[0084] The flowcharts and block diagrams in the accompanying drawings illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to various embodiments of this application. In this regard, each block in a flowchart or block diagram may represent a module, segment, or portion of code containing one or more executable instructions for implementing a specified logical function. It should also be noted that in some alternative implementations, the functions indicated in the blocks may occur in a different order than those indicated in the drawings. For example, two consecutively indicated blocks may actually be executed substantially in parallel, or they may sometimes be executed in reverse order, depending on the functions involved. It is particularly important to note that each block in a block diagram and / or flowchart, and combinations of blocks in block diagrams and / or flowcharts, can be implemented using a dedicated hardware-based system that performs the specified function or operation, or using a combination of dedicated hardware and computer instructions.

[0085] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A valve assembly with optimized linearity, comprising a valve sleeve (10), a valve core (11) arranged in the valve sleeve (10), a crankshaft (12) connected with the valve core (11) and used to drive the valve core (11) to move in the valve sleeve (10), and a motor rotor (13) connected with the crankshaft (12); the crankshaft (12) is eccentric, a plurality of groups of through holes (14) are axially arranged on the valve sleeve (10), a step (21) is arranged on the valve core (11), the step (21) can shield the through holes (14), an unshielded area is a throttling window (22), and movement of the valve core (11) can adjust the area of the throttling window (22); characterized in that, The shape of the through hole (14) is used for non-linear compensation of the motor rotor (13) angle and the throttle window (22) area, so that the motor rotor (13) angle and the throttle window (22) area have a linear change relationship.

2. A linearity optimized valve assembly as in claim 1, characterized by: The length direction of the through hole (14) is parallel to the axial direction of the valve core (11), and the shape of the through hole (14) satisfies the following relationship: ； ； Wherein: x is the distance between the edge of the step (21) and the edge of the through hole (14), h is the height value of the through hole (14) when the distance between the edge of the through hole (14) and the edge of the step (21) is x; y is the area of the throttle window (22) when the distance between the edge of the through hole (14) and the edge of the step (21) is x; r is the eccentricity of the crankshaft (12); α is the rotation angle of the motor rotor (13); b, c, n are constants related to the design of the valve assembly; The shape of the through hole (14) satisfying the above relationship makes the motor rotor (13) angle and the throttle window (22) area have a linear change relationship.

3. A linearity optimized valve assembly as in claim 2, characterized by: When the transmission relationship between the motor rotor (13) and the valve core (11) is crankshaft (12)-connecting rod type or crankshaft (12)-hole type, n is 0.

4. A linearity optimized valve assembly as in claim 2, characterized by: When the transmission relationship between the motor rotor (13) and the valve core (11) is crankshaft (12)-deflection rod type, n is 1 / 2.

5. A linearity optimized valve assembly as in claim 2, characterized by: The valve sleeve (10) is axially arranged with A groups of through holes (14), each group of through holes (14) includes B slot holes (141) distributed along the radial direction of the valve sleeve (10); A is in the range of 1-16, B is in the range of 1-15, and the maximum size of the slot hole (141) is in the range of 0.1 mm-20 mm.

6. A linearity optimized valve assembly as in claim 5, wherein, When B is greater than 1: y represents the sum of the throttle window (22) areas of the B slot holes (141), and h represents the sum of the height values of the B slot holes (141) when the distance between the edge of the through hole (14) and the edge of the step (21) is x.

7. A linearity optimized valve assembly as claimed in claim 5 or 6, characterized in that When B is greater than 1: among the B slot holes (141) of each group of through holes (14), there are Bx regular holes and By irregular holes, and the number of Bx is greater than or equal to 0; The regular hole refers to the height value of the slot hole (141) being a fixed value when the distance between the edge of the slot hole (141) and the edge of the step (21) is any value; the slot hole (141) other than the regular hole is the irregular hole; y represents the sum of the throttle window (22) areas of the Bx regular holes and the By irregular holes, and h represents the sum of the height values of the Bx regular holes and the By irregular holes when the distance between the edge of the through hole (14) and the edge of the step (21) is x.

8. A linearity optimized valve assembly as in claim 1, characterized by: The shape of the through hole (14) is one or more of circular, elliptical, square right angle rounded corner, square right angle inverted corner, square right angle conical curve transition, and square right angle polynomial curve transition.

9. A linearity optimized valve assembly as in claim 8, characterized by: The rounded diameter of the square right angle inverted corner is in the range of 0.05 mm-9.5 mm.

10. A servo valve characterized by: The valve assembly includes the valve assembly according to any one of claims 1-9.

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