CN117404417A

CN117404417A - Valve core assembly and built-in electric control shock absorber comprising same

Info

Publication number: CN117404417A
Application number: CN202210804602.7A
Authority: CN
Inventors: 王申旭; 戴益亮; 滕琳; 段绪伟; 朱柏霖; 季云华; 杜滢君
Original assignee: SAIC Motor Corp Ltd
Current assignee: SAIC Motor Corp Ltd
Priority date: 2022-07-08
Filing date: 2022-07-08
Publication date: 2024-01-16

Abstract

The invention provides a valve core assembly for a built-in electric control shock absorber and the built-in electric control shock absorber comprising the same. The valve core assembly comprises a valve core sheath, an electromagnetic valve assembly, a through-flow assembly and a piston assembly. The flow-through assembly includes a floating piston and a valve body that receives and allows movement in an axial direction. The floating piston receives zero opposing thrust in the axial direction of the working fluid filling the valve core assembly. The fluid passage provided in the valve body and the circumferential groove of the floating piston constitute a flow path through which the working fluid flows. Axial movement of the floating piston may simultaneously change the size of the flow path through-flow cross-section at the interface of the valve body and the floating piston. The working fluid flows through the same flow path during both the recovery stroke and the compression stroke of the spool assembly. The built-in electric control shock absorber has a relatively compact overall structure, and increases the range of damping force provided, thereby improving the adjusting capability.

Description

Valve core assembly and built-in electric control shock absorber comprising same

Technical Field

The invention relates to a valve core assembly used in a built-in electric control shock absorber and the built-in electric control shock absorber comprising the valve core assembly.

Background

In the conventional built-in electronic shock absorber, since a working fluid (e.g., oil) has a pressure difference between upper and lower end surfaces of a floating piston during a compression stroke (downward) and a restoring stroke (upward) of a piston rod (together with a valve element assembly) of the electronic shock absorber, a part of electromagnetic force provided by an electromagnetic valve has to be used to resist the pressure difference, resulting in a reduction of electromagnetic force actually used to resist an elastic force of an adjusting spring (i.e., effective electromagnetic force). This in turn results in a reduced range of damping forces that can be provided by the electronically controlled shock absorber with limited tuning capabilities. In addition, in the conventional built-in electronic control damper, the radial dimension of the electronic control damper is large due to the existence of components (such as a thimble, a guide post and the like) with large radial dimension, so that the space occupied by the electronic control damper in use is increased, and the use range of the electronic control damper is more or less limited.

Therefore, there is a need in the industry for a built-in electrically controlled damper with a large adjustment capability and a compact structure.

In addition, in view of the specific use (e.g., in a vehicle model of a specific need), there is a need for an in-built electronically controlled damper that further provides improved comfort over the electronically controlled dampers described above.

Disclosure of Invention

In order to achieve at least one of the above objects, the present invention provides an improved valve cartridge assembly for an in-built electrically controlled shock absorber. The valve cartridge assembly defines an axial direction and includes a valve cartridge housing, a solenoid valve assembly, a through-flow assembly, and a piston assembly. The solenoid valve assembly is disposed within the spool enclosure and includes a hollow armature reciprocally movable in an axial direction under the influence of an electromagnetic force applied by the solenoid valve assembly. The flow assembly is disposed within the valve core housing and includes a floating piston that moves with the armature, a valve body, and a resilient biasing member. The floating piston is provided with a central through hole and the floating piston itself or the floating piston and the armature together define a circumferential groove such that the resultant force of the opposing thrust forces of the floating piston and the armature, which forces are exerted in the axial direction by the working fluid filling the valve core assembly, is zero. One side of the valve body is abutted with the solenoid valve assembly along the axial direction and is detachably fixed relative to the valve core sheath. The valve body includes: an intermediate region provided with a recess for receiving the floating piston, an outer wall of the floating piston being in close contact with an inner wall of the recess and the floating piston being reciprocally movable in the axial direction within the recess under the influence of electromagnetic force; and a peripheral region surrounding the intermediate region, an outer wall of the peripheral region being in close contact with an inner wall of the spool jacket and the peripheral region being provided with a fluid passage. Wherein the fluid passage and the circumferential groove form a flow path through which the working fluid flows, and the working fluid flows through the same flow path during both the recovery stroke and the compression stroke of the spool assembly. A resilient biasing member is disposed within the solenoid valve assembly and/or the through-flow assembly to apply a force to the armature and/or the through-flow assembly that is opposite the electromagnetic force. Wherein axial movement of the floating piston can change the size of the through-flow cross section of the flow path at the interface of the valve body and the floating piston. The piston assembly abuts a side of the valve body remote from the floating piston and is removably secured relative to the spool cover for allowing working fluid to travel to and from the valve body through the piston assembly.

According to one embodiment of the invention, the circumferential groove has a first bearing surface and a second bearing surface in the axial direction, the projected areas of the first bearing surface and the second bearing surface on a plane perpendicular to the axial direction being equal. Further, the first bearing surface and the second bearing surface are mirror symmetrical about a plane comprising an intersection of the first bearing surface and the second bearing surface.

According to another embodiment of the present invention, a fluid channel includes: at least one first flow passage, each of the at least one first flow passage having a first port in fluid communication with an exterior space located outside of the spool jacket and a first flow passage port capable of fluid communication with the circumferential groove; and at least one second flow passage, each of the at least one second flow passage having a second flow passage opening and a second port, the second flow passage opening being capable of fluid communication with the circumferential groove, the second port being in fluid communication with the fluid space on a side of the valve body remote from the floating piston.

Further, each of the at least one first flow passage extends in a radial direction of the valve body; each of the at least one second flow passage includes a radial segment and an axial segment. The radial segment extends in a radial direction of the valve body to provide a second fluid passage opening. The axial segment is in fluid communication with the radial segment at an end of the radial segment opposite the second flow orifice and extends in an axial direction to provide a second port at an end of the axial segment remote from the radial segment.

Further, when the number of the at least one first flow passage and the at least one second flow passage is plural, the radial sections of the at least one first flow passage and the at least one second flow passage are arranged in an alternately spaced manner along the circumferential direction of the valve body.

Further, the radial segments of the first and second flow passages are each recessed on a side of the valve body facing the solenoid valve assembly such that the solenoid valve assembly and the valve body together define the flow path.

Alternatively, the valve body includes an upper valve body and a lower valve body. The upper valve body is provided with a central through hole and is used for being abutted with the electromagnetic valve assembly. The lower valve body is intended to abut the piston assembly on the side facing away from the upper valve body and is provided with a central recess. Wherein the radial sections of the first flow channel and the second flow channel are open in the form of grooves on the side of the lower valve body facing the upper valve body, the upper valve body and the lower valve body together define a fluid path, and the recess is constituted by a central through hole of the upper valve body and a central recess of the lower valve body.

Alternatively, each of the at least one first flow passage is provided with a first protrusion at the first flow passage opening, respectively, and/or each of the at least one second flow passage is provided with a second protrusion at the second flow passage opening, respectively, such that the working fluid flowing towards the floating piston is diverted to avoid direct impact of the working fluid against the floating piston.

According to a further embodiment of the invention, the recess is in the form of a blind hole or in the form of an assembly of a through hole and an end cap, wherein the end cap is detachably connected to and closes off the end of the through hole remote from the floating piston.

According to a further embodiment of the invention, the valve core jacket is provided with a plurality of radial through holes uniformly arranged on the circumferential wall at the same axial height, at least one of the first ports being in fluid communication with a respective radial through hole of the plurality of radial through holes. The piston assembly is removably inscribed below the plurality of radial through holes to the spool cover, or an outer wall of a lower section of the valve body below the first flow passage is removably inscribed simultaneously to the spool cover and the piston assembly.

Further, in the case where the axial length of the spool cover is insufficient to cover the first port, the outer wall of the upper section of the valve body above the first flow passage and the outer wall of the lower section below the first flow passage are respectively detachably inscribed in the spool cover and the piston assembly which are separated from each other.

Alternatively, the valve body includes at least one flow dividing through bore extending through the valve body in an axial direction, each of the at least one flow dividing through bore fluidly connecting a respective one of the first flow passages with a space located below the valve body. The valve cartridge assembly also includes a compression adjustment assembly disposed between the valve body and the piston assembly for implementing a flow blocking function during a recovery stroke and a flow diverting function during a compression stroke.

Further, the compression adjustment assembly includes a compression adjustment body and a compression adjustment member. The compression adjustment body is provided with an axial through bore extending through the compression adjustment body in an axial direction, the axial through bore allowing fluid communication of a space between the compression adjustment assembly and the valve body and a space between the compression adjustment assembly and the piston assembly. The axial through holes include selected through holes and unselected through holes alternately arranged with each other in a circumferential direction of the compression adjustment assembly. The number of unselected through holes is equal to the number of second flow passages, and each of the unselected through holes is respectively in fluid-tight engagement with one of the second ports. The compression adjustment covers the selected through-hole on a side proximate to the flow-through assembly to achieve a choke function during the return stroke and a shunt function during the compression stroke.

Further, the unselected through-holes extend in the axial direction toward the through-flow assembly with a boss whose end face facing the through-flow assembly is in fluid-tight engagement with the second port. The compression adjustment is a petal-shaped annular sheet including petals and cutouts defined between the petals, each of the cutouts for receiving a respective one of the bosses.

The invention also provides a built-in electric control shock absorber. The electric shock absorber comprises: a cylinder; any one of the aforementioned valve core assemblies configured such that at least a portion of an outer wall of the piston assembly is capable of being in intimate contact with an inner wall of the cylinder, thereby enabling the valve core assembly to be reciprocally switched relative to the cylinder between a compression stroke and a recovery stroke; and the hollow piston rod is connected with the valve core assembly, and a power wire is arranged in the hollow rod cavity of the hollow piston rod in a penetrating way and is used for supplying power to the electromagnetic valve assembly of the valve core assembly.

The present invention provides a built-in electronically controlled damper that is relatively compact and compact in overall structure, since components that are large in radial dimension and thus occupy a large radial space as used in conventional built-in electronically controlled dampers of the prior art are omitted. Furthermore, the built-in electronic control shock absorber provided by the invention realizes decoupling of the oil pressure in the floating piston and the cylinder barrel, increases the effective electromagnetic force acting on the floating piston (reduces or even basically eliminates the requirement of electromagnetic force for resisting the oil pressure difference on two end surfaces of the floating piston), thereby increasing the range of damping force provided by the built-in electronic control shock absorber and improving the adjusting capability of the built-in electronic control shock absorber.

Drawings

In the drawings, the same or similar reference numerals denote the same or similar components. Also, the orientations shown in the drawings are exemplary only and are not intended to limit the use orientation of the electronically controlled damper. The drawings are not necessarily to scale, but may be partially exaggerated to highlight the portions to be emphasized. In the drawings of which there are shown,

fig. 1 is a schematic main body structure of the built-in electronic control shock absorber of the present invention.

FIG. 2 is a cross-sectional view of one embodiment of a spool assembly used in the in-line electronically controlled shock absorber shown in FIG. 1, wherein the left and right sides of the view illustrate the configuration of the second and first flow passages, respectively.

FIG. 3 is a cross-sectional view of one embodiment of a through-flow assembly used in the valve cartridge assembly of FIG. 2.

Fig. 3 (a) -3 (c) are alternative embodiments of the structure shown in circle P in fig. 3.

Fig. 4 is a cross-sectional view of another embodiment of the through-flow assembly shown in fig. 3.

Figure 5 is a schematic view of the flow orifice and the space involved in the valve cartridge assembly of figure 2.

Fig. 6 (a) shows the flow of working fluid in the valve cartridge assembly during the compression stroke of the valve cartridge assembly.

Fig. 6 (b) shows the flow of working fluid in the valve cartridge assembly during the recovery stroke of the valve cartridge assembly.

Fig. 7 (a) and 7 (b) show schematic structural views of the long through hole provided in the spool assembly, respectively.

Fig. 8 and 9 are schematic views of alternative embodiments of the valve cartridge assembly of fig. 2, respectively.

Fig. 10 (a) -10 (c) are diagrams showing the arrangement of the first flow passage and the second flow passage in the through-flow assembly used in the valve cartridge assembly of the present invention.

Fig. 11 (a) and 11 (b) show different embodiments of valve bodies used in the valve cartridge assembly of the present invention, respectively.

Fig. 12 (a) and 12 (b) show alternative embodiments of the assembled structure of the valve cartridge assembly shown in fig. 2, respectively, in which the left and right sides of the drawing each show the structure of the first flow passage.

Fig. 13 (a) and 13 (b) show the case where micro holes are provided in the valve cartridge assembly of the present invention, respectively, wherein both the left and right sides of the drawing show the structure of the second flow passage.

Fig. 14 shows an alternative embodiment of the valve cartridge assembly shown in fig. 8, wherein both the left and right sides of the view show the configuration of the first flow passage.

Fig. 15 shows another alternative embodiment of the valve cartridge assembly shown in fig. 8, wherein both the left and right sides of the view show the configuration of the first flow passage.

Fig. 16 shows another alternative embodiment of the valve cartridge assembly shown in fig. 6 (a) and 6 (b), wherein both the left and right sides of the view show the structure of the first flow passage.

Fig. 17 is an exploded perspective view of the compression adjustment assembly and lower valve body used in fig. 16.

Fig. 18 (a) and 18 (b) are a top perspective view and a bottom perspective view, respectively, of the lower valve body used in fig. 16.

Fig. 19 is a top perspective view of a compression adjustment in the compression adjustment assembly used in fig. 16.

Fig. 20 illustrates an example of a mating engagement between a regulator compression valve body and a second flow passage of the compression adjustment assembly used in fig. 16.

Fig. 21 (a) and 21 (b) are top and bottom perspective views, respectively, of a compression adjustment body in the compression adjustment assembly used in fig. 16.

FIG. 22 illustrates another alternative embodiment of the valve cartridge assembly shown in FIG. 8.

FIG. 23 illustrates another alternative embodiment of the valve cartridge assembly shown in FIG. 2.

Detailed Description

The built-in electronically controlled vibration damper of the present invention will be described with reference to the accompanying drawings.

Referring to fig. 1, the built-in electronically controlled shock absorber 1000 includes a power cord 1, a hollow piston rod 2, a cylinder 3, and a valve cartridge assembly 4. The power cord 1 is connected to and supplies power to the valve cartridge assembly 4 through the hollow rod cavity of the piston rod 2. The valve core assembly 4 may be coupled to the piston rod 2 by means well known to those skilled in the art, such as by a removable means such as a threaded connection or a non-removable means such as friction welding, thereby being capable of reciprocating movement with the piston rod 2 between an upward (referring to the orientation shown in fig. 1) recovery stroke and a downward (referring to the orientation shown in fig. 1) compression stroke. The valve core assembly 4 is disposed in the inner space of the cylinder tube 3 and divides the inner space into a space a above the valve core assembly 4 and a space B below it. The space a and the space B and the spool assembly 4 are filled with a working fluid (e.g., oil). Although the shock absorber is shown in fig. 1 as being of a dual tube type, it will be appreciated by those skilled in the art that it could equally be a monotube shock absorber. Thus, hereinafter, the cylinder 3 may be referred to as either a single cylinder or a double cylinder.

Referring to fig. 2, a valve core assembly 4 for use in the in-line electronically controlled shock absorber shown in fig. 1 is shown. The valve core assembly 4 mainly comprises a valve core sheath 40, a solenoid valve assembly 41, a through flow assembly 42 and a piston assembly 43. A plurality of radial through holes 401 for achieving fluid communication between the inner space and the outer space of the spool sheathing 40 (i.e., the inner space and the space a of the spool assembly 4) are uniformly provided on the circumferential wall of the spool sheathing 40 at the same axial height. The solenoid valve assembly 41 and the through-flow assembly 42 are disposed in abutment with each other within a hollow chamber defined within the spool housing 40, and the piston assembly 43 is removably received within the spool housing 40, such as by a threaded connection, to secure the solenoid valve assembly 41 and the through-flow assembly 42 in an axial direction relative to the spool housing 40. Of course, as is well known to those skilled in the art, the outer diameter of the components (e.g., solenoid valve assembly 41, flow through assembly 42) disposed within the hollow chamber are substantially the same as the inner diameter of the hollow chamber such that substantially no radial movement of these components occurs within the hollow chamber.

The solenoid valve assembly 41 basically includes a generally cup-shaped support ring 411, a solenoid 412 sleeved outside the support ring 411, a cylindrical hollow armature 413 disposed in the interior space C of the support ring 411, and a resilient biasing member (e.g., an upper spring 414 shown in fig. 2) also disposed in the interior space C of the support ring 411 and located between the inside of the top wall of the support ring 411 and the top side of the armature 413. The armature 413 is provided with a central through bore to fluidly connect the interior space C with the space in which the flow assembly 42 is located. The outer diameter of the armature 413 is substantially the same as the inner diameter defined by the inner space of the support ring 411. The presence of the upper spring 414 axially spaces the armature 413 from the support ring 411, but does not cause the armature 413 to completely disengage from the interior space C when moved in an axial direction relative to the support ring 411 under the influence of the electromagnetic force generated by the electromagnetic assembly 41. As will be appreciated by those skilled in the art, the solenoid valve assembly 41 may take on other configurations than that shown in fig. 1, so long as it is capable of applying an appropriate axial force to the flow assembly 42 in a controlled manner.

Referring to fig. 3, the flow assembly 42 basically includes a floating piston 421, a valve body 422 and a resilient biasing member. The resilient biasing member may be any suitable resilient member known to those skilled in the art, and will be described herein by way of example with respect to spring 423. Floating piston 421 is provided with a central through hole 4210 and provided with a circumferential groove 4212 on its outer wall, dividing the outer wall of floating piston 421 into an upper section 4211 and a lower section 4213. The arrangement of the central through hole 4210 and the circumferential groove 4212 is such that the resultant force of the opposing thrust forces of the working fluid filling the valve core assembly 4, which the floating piston 421 receives in the axial direction shown in fig. 3, is zero, i.e. the axial movement of the floating piston is decoupled (independent) from the fluid pressure (e.g. oil pressure). Generally, the central through bore 4210 is spatially separated (i.e., not in fluid communication) from the circumferential groove 4212 due to a structural mating relationship (described in detail below) between the floating piston 421 and the valve body 422, and a pressure differential exists in the two spaces. Thus, the effect of such zero resultant force can be achieved by making the axial resultant force of the working fluid received by the floating piston 421 and the armature 413 at the respective upper and lower end surfaces thereof (i.e., the resultant force of the opposing thrust forces in the axial direction) and the axial resultant force of the working fluid received by the floating piston 421 within the circumferential groove 4212, respectively, zero.

In the embodiment shown in fig. 3, the central through hole 4210 is a straight through hole whose diameter remains constant in the axial direction. The circumferential groove 4212 is preferably an annular groove running in its circumferential direction throughout the outer wall of the floating piston 421. As shown in fig. 3, 3 (a), 3 (b), and 3 (c), the circumferential groove 4212 may have a first pressure-bearing surface 4212U (e.g., a surface that receives fluid pressure upward in the axial direction shown in the drawings without taking radial force into consideration) and a second pressure-bearing surface 4212L (e.g., a surface that receives fluid pressure downward in the axial direction shown in the drawings without taking radial force into consideration), projected areas of the first pressure-bearing surface 4212U and the second pressure-bearing surface 4212L on a plane (e.g., a plane shown by a transverse dotted line in fig. 3, 3 (a), 3 (b), and 3 (c)) extending perpendicular to the axial direction are equal, thereby ensuring that the fluid pressure received by the circumferential groove 4212 in the axial direction is balanced (the resultant force of the opposing thrust forces from the working fluid is zero). Thus, the first pressure bearing surface 4212U and the second pressure bearing surface 4212L may each be planar (as shown in fig. 3 and 3 (a)) or respectively planar or curved (as shown in fig. 3 (b)) or curved (as shown in fig. 3 (c)). Preferably, the first pressure bearing face 4212U and the second pressure bearing face 4212L are mirror symmetrical about a plane including an intersection line of the first pressure bearing face 4212U and the second pressure bearing face 4212L, as shown in fig. 3 (c).

Fig. 4 shows a further embodiment of a floating piston used in the through-flow assembly shown in fig. 3, which differs from fig. 3 in that the floating piston 421' used in the through-flow assembly 42' in fig. 4 has a central through-hole 4210' in the form of a stepped hole. It should be appreciated that the configuration of floating piston 421 'shown in fig. 4 is merely exemplary, and that central throughbore 4210' may have a variety of configurations, so long as the resultant force of the opposing thrust forces from the working fluid experienced by floating piston 421 'in the axial direction within central throughbore 4210' is zero. For the structure of the central through hole 4210', it is required that the bearing surface S is on a plane perpendicular to the axial direction _U 、S _U Sum of projected areas and bearing surface S _L 、S _L ’、S _L "projection planeThe sum of the products is equal.

As shown in fig. 2-4, the valve body 422 includes a central region and a peripheral region disposed about the central region. The intermediate region is provided with a recess 4220 opening towards one side of the floating piston 421, 421 'for receiving/accommodating the floating piston 421, 421' such that an outer wall of the floating piston 421, 421 'is in close contact with an inner wall of the recess 4220 and the floating piston 421, 421' is movable in an axial direction within the recess 4220 with respect to the valve body 422. The recess 4220 may be in the form of a blind hole as shown in fig. 2-4. Although floating pistons 421, 421 'are shown in fig. 2-4 as being entirely within valve body 422, in alternative embodiments, a portion of floating pistons 421, 421' (e.g., at least a portion of upper section 4211) may be disposed within interior space C of support ring 411. Preferably, the outer diameter of the upper section 4211 of the floating pistons 421, 421' and the inner diameter of the inner space C of the support ring 411 may be substantially equal.

The lower spring 423 is disposed in a space D (see fig. 5) defined by the recess 4220 between the floating pistons 421, 421' and the inner bottom wall of the blind hole to space the floating pistons 421, 421' from the bottom side inner wall of the valve body 422 (i.e., the bottom side inner wall of the blind hole) and is capable of timely pushing the floating pistons 421, 421' to move in the axial direction with respect to the valve body 422. Alternatively, in an alternative embodiment, not shown, the recess 4220 may be formed by a through hole and an end cap removably mounted to and thereby blocking the side of the through hole remote from the solenoid valve assembly 411.

As shown in fig. 2-5, two sets of flow passages, a first flow passage set and a second flow passage set, are provided in the peripheral region of the valve body 422. Each flow channel group can comprise at least one flow channel. Each first flow passage 422a in the first flow passage group extends in the radial direction of the spool assembly 4 and is provided with a first port E located radially outward and a radially inward port called a first flow passage F, respectively. After the spool assembly 4 is assembled, the first port E of the at least one first flow passage 422a is in fluid communication with a respective one of the radial through holes 401 of the spool jacket 40. The first fluid port F of each first fluid passage 422a is capable of fluid communication with a circumferential groove 4212 (which defines a circumferential space G, see fig. 5) of the floating piston 421, 421'. Each second flow passage 422b in the second flow passage set includes a radial segment and an axial segment that are in fluid communication with each other. Wherein each radial segment and the first flow passage 422a radially travel in an alternating spaced manner along the circumferential direction of the valve body 422. The radially inner second fluid passage opening H of each radial segment is each capable of fluid communication with the circumferential groove 4212 of the floating piston 421, 421', and the radially outer port of each radial segment is in fluid communication with the upper port of the axial segment. The lower port J of the axial segment (i.e., the second port of the second flow passage 422 b) opens into a space K below the valve body 422 for guiding the working fluid toward the piston assembly 43 during the restoring stroke of the piston rod 2 and receiving the working fluid from the piston assembly 43 during the compression stroke of the piston rod 2.

Fig. 6 (a) and 6 (b) show the flow of working fluid in the valve element assembly 4 during the compression stroke and the return stroke of the valve element assembly 4, respectively.

During the compression stroke, as shown in fig. 6 (a), the working fluid flows from the space B shown in fig. 1 through the piston assembly 43 into the space K shown in fig. 5, and then flows into the space a through the second port J of the second flow passage 422B, the second flow passage H, the circumferential space G of the floating piston, the first flow passage F of the first flow passage 422a, the first port E, and the radial through hole 401 of the spool sheathing 40 in this order.

During the return stroke, as shown in fig. 6 (B), the working fluid flows from the space a into the space K shown in fig. 5 through the radial through hole 401 of the spool cover 40, the first port E of the first flow passage 422a, the first flow passage port F, the circumferential space G of the floating piston, the second flow passage port H of the second flow passage 422B, and the second port J in this order, and then flows into the space B shown in fig. 1 through the piston assembly 43. It can be seen that during the recovery and compression strokes, the working fluid may flow in the same flow path defined in the through-flow assembly 42.

By operating the solenoid valve assembly 40 in the valve cartridge assembly 4 to apply electromagnetic force, the floating piston can be reciprocally moved in the axial direction, thereby changing the flow path constituted by the circumferential groove 4212 of the floating piston and the first flow passage 422a and the second flow passage 422b, i.e., changing the size of the through-flow cross section of the interface (i.e., at least one of the first flow passage port F and the second flow passage port H) of the floating piston 421 and the valve body 422, thereby achieving the size adjustment of the damping force. Specifically, the relative position of armature 413 and floating piston 421 remains unchanged without the application of an electromagnetic force (i.e., solenoid valve assembly 41 is not energized). When the solenoid valve assembly 41 is energized to generate electromagnetic force, the armature 413 is attracted upward/downward in the axial direction due to the electromagnetic force, so that the armature 413 moves upward/downward (wherein the larger the current will result in the larger displacement amount of the armature 413), thereby driving the floating piston 421 to move upward/downward, thereby changing the size of the through-flow cross section of the flow path at least one of the first flow path port F and the second flow path port H. It should be noted that the initial positions of the armature 413 and floating piston 421 (i.e., the positions in which the solenoid valve assembly 41 is not energized) may be preset, which may be accomplished by varying the axial dimensions of the armature 413 and floating piston 421 and the magnitude of the spring preload force. For example, the position shown in fig. 14 may be set as the initial position, and the through-flow cross section is maximized. After the electromagnetic force is applied, the cross-sectional area of the through-flow cross-section gradually decreases as the armature 413 and the floating piston 421 move up/down. As described above, by adjusting the axial dimensions of the armature 413 and the floating piston 421 or the spring preload force, the initial position can be set to be in the limit condition in which the circumferential groove 4212 of the floating piston 421 is completely shielded by the concave portion 4220 of the valve body 422/the inner wall of the support ring 411, at which time the circumferential groove 4221 of the floating piston 421 is not even in communication with one of the first flow passage port F and the second flow passage port H, so that the sectional area of the through-flow section obtained at this time is zero. As the armature 413 moves up/down in the axial direction after energization, the through-flow cross section increases stepwise, resulting in a gradual decrease in damping force.

In view of the above limitations, a normally-open bore may be provided in the spool assembly 4 to permanently (directly or indirectly) fluidly communicate space a with space B or space K. The arrangement of this constant through hole is shown in fig. 11 (a), 7 (a) and 7 (b) as indicated by the symbol Q. The regular through hole Q in fig. 11 (a) directly communicates the first flow passage 422a with the second flow passage 422B adjacent thereto, the regular through hole Q in fig. 7 (a) directly communicates the space a with the space K, and the regular through hole Q in fig. 7 (B) directly communicates the space a with the space B. The size of the normal through hole can be determined by one skilled in the art according to the conventional arrangement.

In an alternative embodiment of the valve cartridge assembly of the present invention, as shown in fig. 8, it is different from the valve cartridge assembly shown in fig. 2 in that the floating piston adopts the structure of the floating piston 421 'shown in fig. 4, and the valve body 422' includes an upper valve body 4221 'and a lower valve body 4222' stacked on each other in the axial direction of the valve cartridge assembly. The upper valve body 4221' has a cross-sectional shape similar to that of the inner space of the spool sheathing 40 and an outer diameter substantially equal to that of the spool sheathing 40, and the upper valve body 4221' is provided with a central through hole and an inner diameter substantially equal to that of the floating piston 421 '. In this case, the radial segments of the first and second flow passages 422a, 422b may be in the form of grooves provided on the side of the lower valve body 4222 'close to the support ring 411, so that after assembly, these grooves constitute respective flow passages with the bottom surface of the upper valve body 4221' located thereabove. The upper valve body 4221 'is provided to transfer the machining accuracy requirement for the lower end surface of the support ring 411 to the lower end surface of the upper valve body 4221' to meet the requirement for through-flow, thereby reducing the machining complexity.

In another alternative embodiment of the valve cartridge assembly of the present invention, as shown in fig. 9, it differs from the valve cartridge assembly shown in fig. 8 in that the upper valve body 4221' is omitted. Alternatively, the upper valve body 4221' is integrated with the support ring 411 as one piece. The radial segments of the first and second flow passages 422a, 422b may also be in the form of grooves provided on the side of the valve body 422 "(which is of the same construction as the lower valve body 4222') adjacent to the support ring 411 so as to form flow passages with the bottom surface of the support ring 411 above it after assembly is completed.

In alternative embodiments, the first and second flow passages 422a, 422b may be provided in a variety of arrangements, primarily in terms of the relative positions of the first and second flow passages F, H. The first fluid passage opening F and the second fluid passage opening H may be at the same height (as shown in fig. 10 (a)). Of course, an alternate spacing arrangement is not necessary. Alternatively, the first and second fluid passage openings F and H may be at different heights, for example, the first fluid passage opening F may be disposed directly above the second fluid passage opening H (as shown in fig. 10 (b)), or both may be staggered (as shown in fig. 10 (c)). All suitable flow passage arrangements are possible as long as the first and second flow passage openings F, H are capable of simultaneous fluid communication with the circumferential groove 4212, thereby enabling working fluid to flow between the spaces a, K. As known to those skilled in the art, the flow passage cross section is not limited to the rectangular cross section shown in fig. 10 (a), 10 (b) and 10 (c).

Although only one of the other flow path groups is shown between adjacent flow paths of the same flow path group in fig. 10 (a) and 10 (c), it is understood that at least two of the other flow path groups may be provided between adjacent two flow paths of the same flow path group.

In an alternative embodiment, as shown in fig. 11 (b), a protrusion 4223 may be provided at the location of the first fluid passage port F and/or the second fluid passage port H, and the axial cross-section of the protrusion 4223 may be triangular with a base toward the middle region of the valve body 422 for diverting the working fluid flowing toward the recess 4220 (i.e., toward the floating pistons 421, 421 ') to avoid direct impact against the floating pistons 421, 421' provided within the recess 4220 during the compression stroke and the recovery stroke of the valve element assembly 4.

Referring to fig. 12 (a) and 12 (b), an alternative embodiment of the valve cartridge assembly 4 shown in fig. 2 is shown. In fig. 12 (a), the spool assembly 4' differs from the spool assembly 4 in fig. 2 in that the length of the spool sheathing 40' in the axial direction of the spool assembly 4' does not exceed the first port E. In other words, the spool sheath 40' does not cover the first port E. In this case, the outer walls of the upper section 422U of the valve body 422 above the first flow passage 422a and the lower section 422L below the first flow passage 422a are detachably inscribed in the spool sheathing 40' and the piston assembly 43, respectively, such as by screw connection. In fig. 12 (b), the spool assembly 4″ differs from the spool assemblies in fig. 2, 8 and 9 in that the outer wall of the lower section 422L (or lower valve body 4222') of the valve body 422, 422″ below the first flow passage 422a is simultaneously removably inscribed in the spool sheathing 40 and the piston assembly 43, such as in a threaded connection.

In an alternative embodiment, it is further contemplated that micro through holes MQ may be provided in the floating piston to facilitate the flow of working fluid between the spaces C, K shown in fig. 5 and the space a shown in fig. 1. The micro through holes may open on the profile of the circumferential groove of the floating piston (as shown in fig. 13 (a)), or may open on the bottom wall of the valve body (as shown in fig. 13 (b)).

In other alternative embodiments, as shown in fig. 14, which differs from the valve core assembly described in fig. 8 in that the armature 413 in the solenoid valve assembly 41 and the floating piston 421' are integrated into a single piece 41u such that both can be reciprocally moved integrally in the axial direction under the electromagnetic force of the solenoid valve assembly 41. Alternatively, in the embodiment shown in fig. 14, when the electromagnetic force acts axially upward, the lower spring may be omitted so that the lower end surface of the integral piece may be in direct contact with the inner bottom wall of the recess 4220; when the electromagnetic force acts downward in the axial direction, the upper spring may be omitted so that the upper end surface of the integral piece may be in direct contact with the inner top wall of the solenoid valve assembly. In another alternative embodiment, not shown, the support ring 411 in the solenoid valve assembly 41 and the valve body 42 may be integrated as one piece with the recess 4220 of the valve body 42 being constituted by a through hole and an end cap removably mounted to and closing off the side of the through hole remote from the solenoid valve assembly 41.

In an alternative embodiment shown in fig. 15, a shim spring 151 and catch 152 may be added to the armature 413 and floating piston 421 'to assemble the two together to further ensure that there is a follower between the armature 413 and floating piston 421' as they move.

FIG. 16 illustrates another alternative embodiment of the valve cartridge assembly shown in FIG. 8. The main difference between the valve cartridge assembly of fig. 16 and the valve cartridge assembly of fig. 8 is that a compression adjustment assembly 44 is further provided between the through-flow assembly 42 and the piston assembly 43 to obtain a better compression adjustment function. The compression adjustment assembly 44 divides the space K shown in fig. 5 into a space K1 between the compression adjustment assembly 44 and the valve body 422' "and a space K2 between the compression adjustment assembly 44 and the piston assembly 43.

Based on the basic configuration of any of the foregoing embodiments of the valve core assembly, when the floating piston in the flow-through assembly 42 moves to the extreme position (i.e., the position of the flow path where the flow-through cross-sections at the first port F and the second port H are smaller), the damping force of the valve core assembly 4 assumes a larger force value due to the smaller flow-through cross-section, both during the recovery stroke and during the compression stroke. For some vehicle types where comfort requirements are high, a greater damping force is required during the recovery stroke to improve performance, but it is desirable that the damping force during the compression stroke be relatively small to improve comfort. For this purpose, the compression adjustment assembly 44 is arranged in a straightforward manner. The purpose of the compression adjustment assembly 44 is to achieve a flow blocking function during the return stroke (i.e., to prevent working fluid flowing through the valve body 422 '"from flowing directly from the first flow passage 422a into the space K2 without passing through the circumferential groove 4212 and the second flow passage 422 b) and a flow dividing function during the compression stroke (i.e., to enable a portion of the working fluid flowing through the valve body 422'" to flow directly from the space K2 into the first flow passage 422a without passing through the circumferential groove 4212 and the second flow passage 422 b).

Fig. 17 shows an exploded perspective view of the valve body 422' "and compression adjustment assembly 44 used in fig. 16. The main difference with the lower valve body 4222 'shown in fig. 8 or the valve body 422″ shown in fig. 9 is that the valve body 422' "is provided with at least one flow dividing through hole 4220 '" extending in the axial direction thereof, each of these flow dividing through holes 4220' "fluidly connecting a respective one of the first flow passages 422a with the space K1. Preferably, in the embodiment shown in fig. 17, the number of the diverting through holes 4220 '"is equal to the number of the first flow passages 422a and the position of each diverting through hole 4220'" corresponds to the position of a corresponding one of the first flow passages 422a, respectively. Further, the valve body 422 '"is provided with a projection 4221'" projecting in the axial direction thereof at a side facing the compression adjustment assembly 44, see fig. 18 (b). Preferably, the tab 4221' "is centrally disposed for positioning the compression adjustment assembly 44.

The compression adjustment assembly 44 disposed immediately below the valve body 422' "includes a compression adjustment member 441 and a compression adjustment body 442. The compression adjustment member 441 may be an annular sheet in a shape including, but not limited to, petals, including petals 4411 and cutouts 4412 defined between the petals 4411, and a central portion of the compression adjustment member 441 is provided with a central through hole 4410 for receiving the protrusion 4221' ", as shown in fig. 19.

Referring to fig. 17 and 21 (a), the compression adjustment body 442 is centrally provided with a central recess 4420 for receiving the tab 4221 '"to assist in achieving positioning of the compression adjustment body 442 and compression adjustment member 441 relative to the valve body 422'". The outer profile of the compression adjustment body 442 is similar to the outer profile of the valve body 422' "such that the outer wall of the compression adjustment body 442 can closely conform to the inner wall of the valve core sheath 40. The compression adjustment body 442 is provided with at least two axial through holes in the circumferential direction on the side facing the valve body 422' "that fluidly connect the space K1 shown in fig. 16 with the space K2.

In the embodiment as shown in fig. 17 and 21 (a), the axial through holes are plural and divided into two groups 4421 and 4422, which are alternately arranged with each other in the circumferential direction. The number of the set of axial through holes 4421 is equal to the number of the second ports J, and each of the set of axial through holes 4421 extends toward the valve body 422' "with a boss 4421-1, respectively. The upper end surface of the boss 4421-1 is for engaging the lower end surface (specifically, the second port J) of the valve body 422' "in a fluid-tight manner so that the axial through-hole 4421 is in fluid communication with the second flow passage 422b, but the working fluid does not leak into the space K1 at the engagement. Alternatively, the boss 4421-1 may be in fluid-tight engagement with the second flow passage 422b in a tab-groove manner as shown in fig. 20.

As shown in fig. 21 (a), the axial through holes 4422 provided between the adjacent two axial through holes 4421 may also extend toward the valve body 422 '"with a boss 4422-1 (but this is not essential), but the boss 4422-1 has an axial height lower than that of the boss 4421-1, and the difference in height therebetween allows the petals 4411 of the compression adjustment member 441 to be accommodated when the compression adjustment member 441 is provided between the compression adjustment body 442 and the valve body 422'". Specifically, each petal 4411 of the compression adjustment member 441 is disposed between two adjacent bosses 4421-1, respectively, so as to cover the axial through-hole 4422 (or the bosses 4422-1, if present) therebetween, to prevent the flow of the working fluid from the space K1 into the space K2 through the axial through-hole 4422 during the restoring stroke, but to allow a portion of the working fluid to flow from the space K2 into the space K1 through the axial through-hole 4422 during the compression stroke, and then to be directly branched into the first flow passage 422a through the branched through-hole 4220' "without passing through the second flow passage 422b and the circumferential groove 4212.

By matching the space dimensions between the petals 4411 and the bosses 4421-1, positioning of the compression adjustment member 441 can be achieved by only providing the bosses 4421-1. In other words, in this case, the protrusion 4221 '"on the valve body 422'", the central through hole 4410 of the compression adjustment member 441, and the central recess 4420 of the compression adjustment body 442 may be omitted. The relative positioning of the compression adjustment member 441 with respect to the valve body 4222' "and the compression adjustment body 442 may be accomplished in a variety of ways. For example, the central through hole of the compression adjustment member 441 is changed to be provided as a protrusion extending toward both sides of the compression adjustment member 441 in the axial direction, and recesses are provided at respective positions on the valve body 422' "and the compression adjustment body 442 to be engaged therewith. All methods of matching positioning that can be envisaged by the person skilled in the art are feasible where applicable.

The side of the compression adjustment body 442 facing away from the compression adjustment 441 is provided with a shaft 4423 extending in the axial direction, and the shaft 4423 may be in the form of a stepped shaft having a large diameter section 4423-1 near the bottom side of the valve body 422 '"and a small diameter section 4423-2 provided opposite thereto from the bottom side of the valve body 422'". The small diameter section 4423-2 is used to mount and position the piston assembly 43, see fig. 16.

In alternative embodiments, not shown, the shaft 4423 of the compression adjustment body 442 may be in the form of a non-stepped shaft, in other words, the shaft 4423 may not include the small diameter section 4423-2. The positioning of the piston assembly 43 may be in the manner shown in fig. 2.

The compression adjustment assembly 44 operates as follows:

when the shock absorber is in the compression stroke, the spool assembly 4 moves downward and working fluid is forced to flow from space B into space K2 through the piston assembly 43. Subsequently, a portion of the working fluid flows into the second flow passage 422b through the axial through-hole 4421 in the compression adjustment body 442, and then flows in accordance with the flow path defined in the spool assembly in which the compression adjustment assembly 44 is not provided. At the same time, another portion of the working fluid may flow into the axial through-hole 4422 in the compression adjustment body 442, thereby pushing the petal 4411 of the compression adjustment 441 upward to flow into the space K1, then into the shunt through-hole 4220 '"in the valve body 422'", then into the first flow passage 4222a, and finally into the space a. This flow path traveled by the other portion of the working fluid forms a diversion path in the compression stroke.

Since the compression adjustment 441 covers the upper end surface of the axial through-hole 4422 in the compression adjustment body 442 (or the upper end surface of the boss 4422-1 in the case where the boss 4422-1 is provided) when the shock absorber is in the restoring stroke, the working fluid cannot flow through the axial through-hole 4422, and at this time, all the working fluid still flows along the flow path (only a portion that flows through the axial through-hole 4421 is increased) in the spool assembly in which the compression adjustment assembly 44 is not provided. In other words, the flow path of the working fluid is increased by only the section of the axial through bore 4421 that passes through the compression adjustment body 442 due to the provision of the compression adjustment assembly 44, as compared to the spool assembly that is not provided with the compression adjustment assembly 44.

Fig. 22 shows an alternative embodiment of the valve cartridge assembly of the present invention, which differs from the embodiment shown in fig. 8 in that a spacer P is provided in the inner space C formed by the support ring 411, the spacer P being provided with a central through hole P _k And is fixed with respect to the support ring 411 so as to divide the inner space C into an upper space C1 and a lower space C2 above and below the spacer P (the orientation shown in fig. 22), respectively. Armature 413 and float The piston 421 is located in the upper space C1 and the lower space C2, respectively, and passes through the central through hole P _k Is connected to the connector 152' to ensure follow-up between the three. An upper spring 414 is provided between the spacer P and the armature 413, and a lower spring 423' is provided between the spacer P and the floating piston 421 to prevent unwanted collision of the various components during movement of the valve core assembly 40.

The connection 152 'is shown in fig. 22 as being in the form of a hollow connecting tube having holes Q1 and Q2 open in the tube wall that fluidly connect the upper spring 414' with the space in which the lower spring 423 'is located through the hollow lumen of the connecting tube 152'. Although the connector 152' is shown in fig. 22 as being in the form of a hollow connecting tube, the connector may take any suitable form, for example, having a diameter smaller than the central through bore P _k Solid connecting rod/rod of diameter of (a)

In another alternative embodiment of the valve cartridge assembly of the present invention, as shown in fig. 23, it differs from the valve cartridge assembly shown in fig. 2 in that the circumferential groove 4212' is not provided by the structure of the floating piston 421 itself, but is formed by the floating piston 421 in conjunction with the armature 413.

The term "circumferential", "cylindrical" structure as used herein does not refer specifically to a structure having a circular cross-section, but may have other cross-sectional shapes, where applicable, such as square, triangular, etc.

Where applicable, the component features in the spool assembly described with reference to one embodiment may be incorporated into another embodiment for use.

Although various embodiments of the present invention have been described with reference to the accompanying drawings, as will be apparent to those skilled in the art, various modifications may be made to the above-described embodiments without departing from the scope as defined in the appended claims. The above embodiments are provided as examples only for illustrating the technical solution of the present invention, and are not intended to limit the scope of the present invention. Features or elements described in one embodiment may be incorporated into another embodiment unless they are inconsistent with existing features or elements in the other embodiment.

Claims

1. A spool assembly for a built-in electronically controlled shock absorber, the spool assembly defining an axial direction and comprising:

a valve core sheath;

a solenoid valve assembly disposed within the spool enclosure and including a hollow armature reciprocally movable in the axial direction under the influence of electromagnetic force applied by the solenoid valve assembly;

The through-flow component is arranged in the valve core sheath and comprises:

a floating piston moving with the armature, the floating piston being provided with a central through hole, and the floating piston itself or the floating piston and the armature together defining a circumferential groove such that a resultant force of opposing thrust forces of the floating piston and the armature, which are received in the axial direction by a working fluid filling the valve core assembly, is zero;

a valve body having one side thereof abutted with the solenoid valve assembly in the axial direction and detachably fixed with respect to the spool sheathing, the valve body comprising:

an intermediate region provided with a recess for receiving the floating piston, an outer wall of the floating piston being in close contact with an inner wall of the recess and the floating piston being reciprocally movable in the axial direction within the recess under the influence of the electromagnetic force; and

a peripheral region surrounding the intermediate region, an outer wall of the peripheral region being in close contact with an inner wall of the spool jacket and the peripheral region being provided with a fluid passage,

wherein the fluid passage and the circumferential groove constitute a flow path through which the working fluid flows, and the working fluid flows through the same flow path during both a recovery stroke and a compression stroke of the spool assembly; and

A resilient biasing member disposed within the solenoid valve assembly and/or the through-flow assembly to apply a force to the armature and/or the through-flow assembly that is opposite the electromagnetic force;

wherein axial movement of the floating piston is capable of changing the size of the through-flow cross section of the flow path at the interface of the valve body and the floating piston; and

and the piston assembly is abutted with one side of the valve body away from the floating piston and is detachably fixed relative to the valve core sheath, and is used for allowing the working fluid to pass to and from the valve body through the piston assembly.

2. The valve cartridge assembly of claim 1, wherein the circumferential groove has a first bearing surface and a second bearing surface along the axial direction, the first bearing surface and the second bearing surface having equal projected areas on a plane perpendicular to the axial direction.

3. The valve cartridge assembly of claim 2, wherein the first pressure bearing surface and the second pressure bearing surface are mirror symmetric about the plane including an intersection of the first pressure bearing surface and the second pressure bearing surface.

4. The valve cartridge assembly of claim 1, wherein the fluid passage comprises:

at least one first flow passage, each of the at least one first flow passage having a first port in fluid communication with an exterior space located outside of the spool jacket and a first flow passage port in fluid communication with the circumferential groove; and

at least one second flow passage, each of the at least one second flow passage having a second flow passage opening and a second port, the second flow passage opening being capable of fluid communication with the circumferential groove, the second port being in fluid communication with a fluid space located on a side of the valve body remote from the floating piston.

5. The valve cartridge assembly of claim 4,

each of the at least one first flow passage extends in a radial direction of the valve body;

each of the at least one second flow passage each includes:

a radial segment extending in a radial direction of the valve body to provide the second fluid passage opening; and

an axial segment in fluid communication with the radial segment at an end of the radial segment opposite the second flow orifice and extending in the axial direction to provide the second port at an end of the axial segment remote from the radial segment.

6. The valve cartridge assembly of claim 5, wherein when the number of the at least one first flow passage and the at least one second flow passage are each plural, radial segments of the at least one first flow passage and the at least one second flow passage are disposed in an alternately spaced manner along a circumferential direction of the valve body.

7. The valve cartridge assembly of claim 5 or 6, wherein the radial segments of the first and second flow passages are each in the form of a groove open on a side of the valve body facing the solenoid valve assembly such that the solenoid valve assembly and the valve body together define the flow path.

8. The valve cartridge assembly of claim 5 or 6, wherein the valve body comprises:

the upper valve body is provided with a central through hole and is used for being abutted with the electromagnetic valve assembly; and

a lower valve body for abutment with the piston assembly on a side facing away from the upper valve body and provided with a central recess,

wherein radial sections of the first flow passage and the second flow passage are open in the form of grooves on a side of the lower valve body facing the upper valve body, the upper valve body and the lower valve body together define the fluid path, and the recess is constituted by a central through hole of the upper valve body and a central recess of the lower valve body.

9. The valve cartridge assembly of any one of claims 4-6, wherein,

each of the at least one first flow passage is provided with a first protrusion at the first flow passage opening, and/or

Each of the at least one second flow passage is provided with a second protrusion at the second flow passage opening,

thereby diverting the working fluid flowing toward the floating piston to avoid direct impact of the working fluid on the floating piston.

10. The valve cartridge assembly of any one of claims 1-6, wherein the recess is in the form of a blind hole or in the form of an assembly of a through bore and an end cap, wherein the end cap is removably connected to and blocks an end of the through bore remote from the floating piston.

11. The valve cartridge assembly of any one of claims 4-6, wherein,

a plurality of radial through holes are uniformly arranged on the circumferential wall of the valve core sheath at the same axial height, and at least one of the first ports is in fluid communication with a corresponding radial through hole in the plurality of radial through holes;

the piston assembly is removably inscribed under the plurality of radial through holes to the spool jacket, or an outer wall of a lower section of the valve body below the first flow passage is removably inscribed simultaneously to the spool jacket and the piston assembly.

12. The valve cartridge assembly of any one of claims 4-6, wherein an outer wall of an upper section of the valve body above the first flow passage and an outer wall of a lower section below the first flow passage are detachably inscribed in the valve cartridge jacket and the piston assembly, respectively, that are separated from each other, in the event that an axial length of the valve cartridge jacket is insufficient to cover the first port.

13. The valve cartridge assembly of any one of claims 4-6, wherein the valve body includes at least one flow-splitting through bore extending therethrough in the axial direction, each of the at least one flow-splitting through bores fluidly communicating a respective one of the first flow passages with a space located below the valve body; and

the valve cartridge assembly also includes a compression adjustment assembly disposed between the valve body and the piston assembly for implementing a choke function during the recovery stroke and a shunt function during the compression stroke.

14. The valve cartridge assembly of claim 13, wherein the compression adjustment assembly comprises:

A compression adjustment body provided with axial through holes extending through the compression adjustment body in the axial direction, the axial through holes allowing fluid communication between a space between the compression adjustment assembly and the valve body and a space between the compression adjustment assembly and the piston assembly, the axial through holes including selected through holes and unselected through holes alternately arranged with each other in a circumferential direction of the compression adjustment assembly, the number of unselected through holes being equal to the number of second flow passages, and each of the unselected through holes being each engaged with one of the second ports in a fluid-tight manner; and

a compression adjustment covering the selected through-hole on a side proximate to the flow-through assembly to effect the choke function during the return stroke and the shunt function during the compression stroke.

15. The valve cartridge assembly of claim 13, wherein the unselected through-holes extend along the axial direction toward the through-flow assembly with a boss having an end face facing the through-flow assembly in fluid-tight engagement with the second port;

The compression adjustment is a petal-shaped annular sheet including petals and cutouts defined between the petals, each of the cutouts for receiving a respective one of the bosses.

16. A built-in electric control shock absorber, characterized in that the built-in electric shock absorber comprises:

a cylinder;

the valve cartridge assembly of any preceding claim, arranged such that at least part of an outer wall of the piston assembly is capable of intimate contact with an inner wall of the bore, thereby enabling the valve cartridge assembly to be reciprocally switched relative to the bore between the compression and recovery strokes; and

the hollow piston rod is connected with the valve core assembly, and a power wire is arranged in a hollow rod cavity of the hollow piston rod in a penetrating mode and used for supplying power to the electromagnetic valve assembly of the valve core assembly.