Variable displacement compressor flow control valve based on valve port adaptive wear compensation

Abstract

This invention discloses a variable displacement compressor flow control valve based on valve port adaptive wear compensation, belonging to the technical field of automotive air conditioning compressor control valves. It includes a bellows assembly, an electromagnetic drive assembly, a valve body with a through cavity, a valve core floating within the through cavity and having a through flow channel, and an inner valve stem floating within the through flow channel; a sealing ring three is sleeved around the outer periphery of the valve core; a valve port one is provided on the outer wall of the valve core, which can overlap with a valve port two provided on the inner wall of the through cavity; the valve body is provided with a Ps port communicating with a first cavity, a Pd port communicating with a second sub-cavity one, and a Pc port communicating with a second sub-cavity two; the electromagnetic drive assembly includes a push rod and a fixed iron core movably sleeved around the outer periphery of the push rod. This invention's variable displacement compressor flow control valve based on valve port adaptive wear compensation solves the problem of reduced compressor maximum displacement due to main valve port wear and leakage after long-term use in existing control valves.

Description

Technical Field

[0001] This invention belongs to the technical field of automotive air conditioning compressor control valves, specifically relating to a variable displacement compressor flow control valve based on valve port adaptive wear compensation. Background Technology

[0002] The control valve of the variable displacement compressor used in automotive air conditioning compressors has three standard pressure ports: Suction Pressure (Ps), Crankcase Pressure (Pc), and Discharge Pressure (Pd). The piston stroke adjustment of the compressor is closely related to the crankcase / swashplate pressure: the lower the crankcase / swashplate pressure, the longer the compressor piston stroke, and the larger the cooling capacity; conversely, the shorter the compressor piston stroke, the smaller the cooling capacity. The function of the control valve on the automotive air conditioning compressor is to control the refrigerant flow from the Pd port to the Pc port of the crankcase / swashplate, thereby controlling the crankcase / swashplate pressure and thus adjusting the compressor's cooling capacity.

[0003] However, after a period of long-term use, the existing control valves of the car air conditioning compressor often wear down due to the long-term contact and collision between the valve core tip and the valve body cone surface. This causes a small amount of gaseous medium to still flow to the Pc port through the valve port leakage point when the electronically controlled valve closes the valve port with a large current. As a result, the pressure in the compressor crankcase / swashplate box cannot be completely reduced, which causes the compressor piston to be unable to reach its maximum working stroke. Consequently, the cooling capacity of the compressor does not reach the maximum design level, resulting in the car occupants feeling that the air conditioning is not cold enough. Summary of the Invention

[0004] The purpose of this invention is to overcome the shortcomings of the prior art and provide a variable displacement compressor flow control valve based on valve port adaptive wear compensation, which solves the problem that the maximum displacement of the compressor decreases due to wear and leakage of the main valve port after long-term use of the existing control valve.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows: a variable displacement compressor flow control valve based on valve port adaptive wear compensation, comprising a valve body having a through cavity, a bellows assembly sealed to one end of the through cavity, an electromagnetic drive assembly sealed to the other end of the through cavity, a valve core floating in the through cavity and having a through flow channel, and an inner valve stem floating in the through flow channel; The valve core is fitted with a sealing ring three for separating the through cavity into a first cavity and a second cavity; the valve core is provided with a valve port one on the outer wall inside the second cavity, the valve port one can overlap with a valve port two provided on the inner wall of the through cavity, and the valve port one and the valve port two form a main valve port for separating the second cavity into a second sub-cavity one and a second sub-cavity two; The valve body is provided with a Ps port connected to the first cavity, a Pd port connected to the first second sub-cavity, and a Pc port connected to the second second sub-cavity. The electromagnetic drive assembly includes a push rod and a fixed iron core movably sleeved on the outer periphery of the push rod. The valve core can float until one end of it abuts against the end of the fixed iron core to block the communication between the through flow channel and the first cavity. The end of the bellows assembly can elastically abut against the other end of the valve core to block the communication between the through flow channel and the second sub-cavity. The push rod can drive the valve core to press down on the bellows assembly, or drive the inner valve rod to move relative to the valve core until its end abuts against the end of the bellows assembly and disengages from the end of the valve core.

[0006] Optionally, the end of the push rod abuts against the end face of the inner valve rod; the outer periphery of the valve core is movably sleeved with a return spring that is elastically supported at both ends on the valve core and the inner wall of the first cavity, respectively, and the return spring is used to drive the valve core to float until one end of it faces the end of the fixed iron core; the outer periphery of the inner valve rod is movably sleeved with a support spring that is elastically supported at both ends on the inner valve rod and the inner wall of the through flow channel, respectively, and the support spring is used to drive the inner valve rod to float relative to the valve core until its top end abuts against the push rod.

[0007] Optionally, the longitudinal section of the inner valve stem along its axial direction is T-shaped, and the inner valve stem includes a column head for supporting the support spring and a rod body portion that can abut against the bellows assembly; The column head is fitted with the inner wall of the through flow channel with a clearance, the outer diameter of the rod body is smaller than the outer diameter of the column head, the distance between the outer wall of the rod body and the inner wall of the through flow channel is greater than the distance between the outer wall of the column head and the inner wall of the through flow channel, and a flow groove with its bottom tangent to the outer wall of the rod body is provided on the column head.

[0008] Optionally, a retaining ring that can be movably fitted around the outer periphery of the column head is fixedly embedded at the top of the through channel, and the retaining ring can be pressed against the shoulder surface of the step provided on the column head along the elastic force direction of the support spring.

[0009] Optionally, the electromagnetic drive assembly further includes a moving iron core sleeved around the outer periphery of the top rod, a guide sleeve movably covered around the outer periphery of the moving iron core and sleeved around the outer periphery of the fixed iron core, a housing covered around the outer periphery of the guide sleeve, and an electromagnetic coil embedded between the housing and the guide sleeve. The moving iron core is clearance-fitted with the inner wall of the guide sleeve, the open end of the housing is sealed to the end opening of the valve body, and a sealing ring is provided between the guide sleeve and the housing.

[0010] Optionally, a sealed cavity is formed between the guide sleeve and the fixed iron core, and a gap is reserved between the push rod and the fixed iron core for connecting the sealed cavity and the through cavity.

[0011] Optionally, the outer periphery of the housing and the valve body is provided with a plurality of sealing rings.

[0012] Optionally, a filter component is provided inside the Pd port.

[0013] Optionally, the fixed iron core, the top rod, the inner valve rod, the valve core, and the bellows assembly are arranged coaxially.

[0014] Compared with the prior art, the beneficial effects achieved by the present invention are as follows: by adding a passage structure that can be controlled to open and close by displacement of the push rod, the gas in the second sub-cavity can flow back upward from the gap between the bottom end of the valve core and the top end of the bellows assembly to the through flow channel, and can be connected to the first cavity through the gap between the top end of the valve core and the fixed iron core, thereby being quickly discharged through the Ps port. This allows the pressure in the swashplate cavity to be quickly reduced even when wear occurs in the first and second valve ports, enabling the compressor to operate at its maximum displacement. Attached Figure Description

[0015] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0016] Figure 1 This is a cross-sectional view of the flow control valve for a variable displacement compressor when the main valve port is closed, according to a preferred embodiment of the present invention. Figure 2 This is a preferred embodiment of the present invention. Figure 1 A magnified structural diagram at point B; Figure 3 This is a preferred embodiment of the present invention. Figure 1 A magnified structural diagram at point C; Figure 4 This is a cross-sectional view of the flow control valve for a variable displacement compressor when the secondary valve port is closed and the main valve port is open, according to a preferred embodiment of the present invention. Figure 5 This is a preferred embodiment of the present invention. Figure 4A structural schematic diagram of a partially enlarged structural diagram at point D; Figure 6 This is a preferred embodiment of the present invention. Figure 4 A magnified structural diagram at point E; Figure 7 This is a top view of the upper column head of the inner valve stem in a preferred embodiment of the present invention; The components are as follows: 1. Valve body; 101. First cavity; 102. Second sub-cavity one; 103. Second sub-cavity two; 104. Valve port two; 105. Ps port; 106. Pd port; 107. Pc port; 2. Bellows assembly; 3. Valve core; 301. Through flow channel; 302. Valve port one; 4. Inner valve stem; 401. Column head; 4011. Flow groove; 4012. Step shoulder; 402. Stem body; 5. Sealing ring three; 6. Top rod; 7. Fixed iron core; 8. Return spring; 9. Support spring; 10. Retaining ring; 11. Moving iron core; 12. Guide sleeve; 13. Housing; 14. Electromagnetic coil; 15. Sealing ring one; 16. Sealing ring two; 17. Filter assembly; 18. Secondary valve port one; 19. Secondary valve port two; 20. Main valve port. Detailed Implementation

[0017] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. These drawings are simplified schematic diagrams, which are only used to illustrate the basic structure of the present invention and therefore only show the components relevant to the present invention.

[0018] It should be noted that if directional indicators (such as up, down, bottom, top, etc.) are involved in this embodiment, these directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly. The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, features defined with "first" and "second" may explicitly or implicitly include one or more of that feature. Unless otherwise explicitly specified and limited, the terms "set," "connected," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; 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 invention can be understood according to the specific circumstances. Example 1

[0019] like Figures 1-7As shown, a flow control valve for a variable displacement compressor based on valve port adaptive wear compensation includes a valve body 1 with a through cavity, a bellows assembly 2 sealed to one end of the through cavity, an electromagnetic drive assembly sealed to the other end of the through cavity, a valve core 3 floatingly disposed within the through cavity and having a through flow channel 301, and an inner valve stem 4 floatingly disposed within the through flow channel 301. Specifically, in this embodiment, the outer wall of the valve core 3 is clearance-fitted with the inner wall of the through cavity, allowing the valve core 3 to perform precise linear movement relative to the through cavity. It should be noted that a sealing ring 5 is sleeved around the outer periphery of the valve core 3, capable of moving synchronously with the valve core 3, thereby enabling the sealing ring 5 to divide the through cavity into a first cavity 101 and a second cavity. Furthermore, a valve port portion 302 is provided on the outer wall of the valve core 3 within the second cavity. This valve port portion 302 can overlap with a valve port portion 104 provided on the inner wall of the through cavity. A main valve port 20 is formed between the valve port portion 302 and the valve port portion 104 to separate the second cavity into a second sub-cavity 102 and a second sub-cavity 103. That is, when the valve port portion 302 abuts against the valve port portion 104, the communication between the second sub-cavity 102 and the second sub-cavity 103 is disconnected. Meanwhile, in this embodiment, the electromagnetic drive assembly includes a push rod 6 and a fixed iron core 7 movably sleeved around the outer periphery of the push rod 6, specifically as follows... Figure 4 , Figure 5 , Figure 6 As shown, when the valve core 3 floats until one end abuts against the end of the fixed iron core 7, it can block the connection between the through flow channel 301 and the first cavity 101. A secondary valve port 18 for connecting the through flow channel 301 and the first cavity 101 can be formed between the top of the valve core 3 and the top of the fixed iron core 7, and at this time the opening of the main valve port 20 reaches its maximum. When one end of the bellows assembly 2 elastically abuts against the other end of the valve core 3, it can block the connection between the through flow channel 301 and the second sub-cavity 103. A secondary valve port 19, which connects the through flow channel 301 and the second sub-cavity 103, can be formed between the bottom end of the valve core 3 and the top end of the bellows assembly 2. When the push rod 6 drives the valve core 3 to press down on the bellows assembly 2, the opening of the main valve port 20 will continuously decrease as the valve port 302 and the valve port 104 approach each other. When the valve port 302 abuts against the valve port 104, the main valve port 20 will be completely closed, and the secondary valve port 18 will reach its maximum opening. Then, when the push rod 6 drives the inner valve stem 4 to move relative to the valve core 3, since the position of the valve core 3 is limited by the valve port 104, the push rod 6 can push the end of the bellows assembly 2 open to disengage from the end of the valve core 3, thereby opening the secondary valve port 19 and increasing its opening. It should be noted that, since the inner valve stem 4 is floatingly disposed within the through-flow channel 301, there is a gap between the outer wall of the inner valve stem 4 and the inner wall of the through-flow channel 301 for connecting the second sub-cavity 103 and the first cavity 101. In this embodiment, as... Figure 1As shown, the valve body 1 is provided with a Ps port 105 connected to the first cavity 101, a Pd port 106 connected to the second sub-cavity 102, and a Pc port 107 connected to the second sub-cavity 2 103.

[0020] In actual use, Ps port 105 is connected to the compressor's suction port, Pc port 107 is connected to the compressor's crankcase / swashplate case, and Pd port 106 is connected to the compressor's discharge port. When the electromagnetic drive assembly is not energized, the valve core 3 can float until one end abuts against the end of the fixed iron core 7, thereby closing the auxiliary valve port 18 and causing the main valve port 20 to reach its maximum opening. Pc port 107 and Pd port 106 can then be connected through the second cavity. When the electromagnetic drive assembly is energized and the compressor needs to operate at variable displacement, the electromagnetic drive assembly can move the drive rod 6, thereby driving the valve core 3 to press down on the bellows assembly 2, thus adjusting the opening of the main valve port 20 and achieving variable displacement control between Pc port 107 and Pd port 106. It should be noted that when the compressor needs to operate at a large displacement, such as... Figure 2 As shown, after the main valve port 20 is closed (valve port 1 302 abuts against valve port 2 104), the push rod 6 drives the inner valve rod 4 downward and forces the lower end face of the valve core 3 to disengage from the upper end face of the bellows assembly 2. This causes the gas in the second sub-cavity 2 103 to flow back upward from the auxiliary valve port 2 19 through the through-flow channel 301, auxiliary valve port 1 18, and the first cavity 101 to the Ps port 105 for discharge. This further reduces the pressure in the swashplate cavity, ensuring that the compressor is in its maximum displacement state. Therefore, even if the main valve port 20 experiences wear that reduces the sealing accuracy of the valve port, and a small amount of gaseous medium leaks through the main valve port 20 into the second sub-cavity 2 103 connected to the Pc port 107, it can still cause the pressure in the compressor crankcase / swashplate box to drop completely, and the compressor piston can still be in its maximum working stroke.

[0021] The above, such as Figure 1As shown, the end of the push rod 6 abuts against the end face of the inner valve stem 4; the outer periphery of the valve core 3 is movably sleeved with a return spring 8, which is elastically supported at both ends on the valve core 3 and the inner wall of the first cavity 101, respectively. The return spring 8 is used to drive the valve core 3 to float until one end faces the end of the fixed iron core 7; the outer periphery of the inner valve stem 4 is movably sleeved with a support spring 9, which is elastically supported at both ends on the inner valve stem 4 and the inner wall of the through flow channel 301, respectively. The support spring 9 is used to drive the inner valve stem 4 to float relative to the valve core 3 until its top end faces the push rod 6. It should be noted that in this embodiment, the push rod 6 only directly applies force to the inner valve stem 4. And when the push rod 6 presses down on the inner valve stem 4, the reaction force of the support spring 9 on the inner valve stem 4 is greater than the reaction force of the return spring 8 on the valve core 3, thereby causing the return spring 8 to compress and deform before the support spring 9. Therefore, by using the push rod 6 to drive the inner valve stem 4 downward, the valve core 3 is simultaneously driven downward, thereby opening the secondary valve port 18 and regulating the opening of the main valve port 20. After the valve port 302 abuts against the valve port 104, the push rod 6 continues to drive the inner valve stem 4 downward. At this time, the valve core 3 and the valve body 1 will remain relatively stationary, while the support spring 9 will undergo compression deformation under the pressure of the push rod 6, thereby causing the inner valve stem 4 to abut against the bellows assembly 2 until its end separates from the end of the valve core 3, thus opening the secondary valve port 19. When the push rod 6 fails, the support spring 9 and the return spring 8 will drive the valve core 3 and the inner valve stem 4 to return upward until the valve core 3 floats up to its top abutting against the fixed iron core 7 and the top of the bellows assembly 2 abutting against the bottom of the valve core 3.

[0022] As described above, the filter assembly 17 can be a filter screen, filter nozzle or other conventional filter components in the conventional technology of the field, to block dust, fibers and other debris from entering the through cavity.

[0023] The above, such as Figure 4 As shown, the longitudinal section of the inner valve stem 4 along its axial direction is T-shaped. The inner valve stem 4 includes a column head 401 for supporting the support spring 9 and a rod body 402 that can abut against the bellows assembly 2. The column head 401 is clearance-fitted with the inner wall of the through flow channel 301 to ensure the accuracy of the linear movement of the inner valve stem 4 relative to the valve core 3 under the downward pressure of the top rod 6. In this embodiment, the outer diameter of the rod body 402 is smaller than the outer diameter of the column head 401, and the distance between the outer wall of the rod body 402 and the inner wall of the through flow channel 301 is greater than the distance between the outer wall of the column head 401 and the inner wall of the through flow channel 301. The column head 401 has a flow groove 4011 whose bottom is tangent to the outer wall of the rod body 402 to increase the rate at which the gaseous medium passes through the through flow channel 301 when the secondary valve port 18 and the secondary valve port 2 19 are opened.

[0024] Furthermore, such as Figure 4 , Figure 7As shown, in this embodiment, a retaining ring 10 that can be movably sleeved on the outer periphery of the column head 401 is fixedly embedded at the top of the through flow channel 301, and the retaining ring 10 can be pressed against the stepped shoulder surface 4012 provided on the column head 401 along the elastic force direction of the support spring 9, so as to limit the range of motion of the inner valve rod 4 relative to the through flow channel 301, and avoid the inner valve rod 4 from being abnormally misaligned due to rapid reset after the top rod 6 fails.

[0025] In this embodiment, the fixed iron core 7, push rod 6, inner valve stem 4, valve core 3, and bellows assembly 2 are arranged coaxially to ensure that the transmission force between each component is evenly aligned, avoid uneven wear and jamming of push rod 6, valve core 3, and inner valve stem 4, improve the opening and closing control accuracy and sealing reliability of each valve port, and at the same time reduce vibration wear and extend service life. Example 2

[0026] Based on Example 1, such as Figure 1 As shown, in this embodiment, the electromagnetic drive assembly further includes a moving iron core 11 sleeved around the outer periphery of the push rod 6, a guide sleeve 12 movably covering the outer periphery of the moving iron core 11 and sleeved around the outer periphery of the fixed iron core 7, a housing 13 covering the outer periphery of the guide sleeve 12, and an electromagnetic coil 14 embedded between the housing 13 and the guide sleeve 12. The moving iron core 11 and the inner wall of the guide sleeve 12 are in clearance fit, allowing the moving iron core 11 to slide relative to the guide sleeve 12, and the moving iron core 11 and the push rod 6 can move synchronously. The open end of the housing 13 is sealed to the end opening of the valve body 1, and a sealing ring 15 is provided between the guide sleeve 12 and the housing 13, thereby achieving a sealed connection between the electromagnetic drive assembly and the other end of the through cavity.

[0027] Furthermore, in this embodiment, a sealed cavity is formed between the guide sleeve 12 and the fixed iron core 7, which can be sealed and communicated with the through cavity, and a gap is reserved between the push rod 6 and the fixed iron core 7 for connecting the sealed cavity and the through cavity. Therefore, the pressure generated by the gaseous medium in the through cavity can act on the top of the push rod 6 through this gap, thereby balancing the pressure of the gaseous medium acting on the bottom of the push rod 6.

[0028] Furthermore, in this embodiment, when the electromagnetic coil 14 is energized, the moving iron core 11 can move downward under the electromagnetic force generated by the electromagnetic coil 14, thereby driving the valve core 3 to press down the bellows assembly 2 and adjust the opening of the main valve port 20 through the push rod 6. It should be noted that the displacement of the valve core 3 depends on the balance point formed by the electromagnetic force, the force of the return spring 8, the reaction force of the spring of the bellows assembly 2 itself, and the force of the gaseous medium on the bellows assembly 2, thereby causing the main valve port 20 to reach an opening of an accurate flow rate.

[0029] The bellows assembly 2 used in this embodiment is existing technology. That is, when the compressor intake pressure (Ps) changes due to changes in the ambient engine speed during vehicle operation, the bellows on the bellows assembly 2 will lengthen or shorten due to the change in Ps. In conjunction with the electromagnetic drive assembly, variable displacement control of the compressor can be achieved.

[0030] Furthermore, in this embodiment, such as Figure 1 As shown, the outer periphery of the housing 13 and the valve body 1 is fitted with several sealing rings 16 to increase the sealing performance of the variable displacement compressor flow control valve assembled on the compressor in this technical solution.

[0031] Working principle: When the electromagnetic coil 14 is energized, the moving iron core 11 can move downward under the electromagnetic force generated by the electromagnetic coil 14, thereby pressing down the inner valve stem 4 through the push rod 6. When the push rod 6 presses down the inner valve stem 4, with the cooperation of the support spring 9 and the return spring 8, the push rod 6 can drive the inner valve stem 4 to move downward at the same time, simultaneously driving the valve core 3 to move downward, thereby achieving the effect of opening the auxiliary valve port 18 and regulating the opening degree of the main valve port 20. Once valve port 302 abuts against valve port 104, the inner valve stem 4 continues to move downward via push rod 6. The valve core 3 and valve body 1 remain relatively stationary, while the support spring 9 undergoes compression deformation under the pressure of push rod 6. This causes the inner valve stem 4 to abut against bellows assembly 2 until its end separates from the end of valve core 3, thereby opening secondary valve port 19. This allows gas in the second sub-cavity 103 to flow back upwards from secondary valve port 19 through through-flow channel 301, secondary valve port 18, and the first cavity 101 to Ps port 105 for discharge. This further reduces the pressure in the swashplate chamber, ensuring the compressor operates at maximum displacement. This prevents the compressor piston from operating at its maximum stroke and the cooling capacity from falling below the design maximum level due to insufficient pressure reduction in the crankcase / swashplate chamber.

[0032] Based on the preferred embodiments of the present invention described above, those skilled in the art can make various changes and modifications without departing from the inventive concept. The technical scope of this invention is not limited to the contents of the specification, but must be determined according to the scope of the claims.

Claims

1. A flow control valve for a variable displacement compressor based on valve port adaptive wear compensation, characterized in that: It includes a valve body (1) with a through cavity, a bellows assembly (2) sealed to one end of the through cavity, an electromagnetic drive assembly sealed to the other end of the through cavity, a valve core (3) floating in the through cavity and having a through flow channel (301), and an inner valve stem (4) floating in the through flow channel (301). The valve core (3) is fitted with a sealing ring three (5) for separating the through cavity into a first cavity (101) and a second cavity; the valve core (3) is provided with a valve port part one (302) on the outer wall inside the second cavity, the valve port part one (302) can overlap with the valve port part two (104) provided on the inner wall of the through cavity, and a main valve port (20) is formed between the valve port part one (302) and the valve port part two (104) for separating the second cavity into a second sub-cavity one (102) and a second sub-cavity two (103); The valve body (1) is provided with a Ps port (105) connected to the first cavity (101), a Pd port (106) connected to the second sub-cavity one (102), and a Pc port (107) connected to the second sub-cavity two (103). The electromagnetic drive assembly includes a push rod (6) and a fixed iron core (7) movably sleeved on the outer periphery of the push rod (6). The valve core (3) can float so that one end of it abuts against the end of the fixed iron core (7) to block the communication between the through flow channel (301) and the first cavity (101). The end of the bellows assembly (2) can elastically abut against the other end of the valve core (3) to block the communication between the through flow channel (301) and the second sub-cavity (103). The push rod (6) can drive the valve core (3) to press down the bellows assembly (2), or drive the inner valve rod (4) to move relative to the valve core (3) until its end abuts against the end of the bellows assembly (2) and disengages from the end of the valve core (3).

2. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 1, characterized in that: The end of the top rod (6) abuts against the end face of the inner valve rod (4); the outer periphery of the valve core (3) is movably sleeved with a return spring (8) that is elastically supported at both ends on the inner wall of the valve core (3) and the first cavity (101), and the return spring (8) is used to drive the valve core (3) to float to one end facing the end of the fixed iron core (7); the outer periphery of the inner valve rod (4) is movably sleeved with a support spring (9) that is elastically supported at both ends on the inner valve rod (4) and the inner wall of the through flow channel (301), and the support spring (9) is used to drive the inner valve rod (4) to float relative to the valve core (3) to its top end facing the top rod (6).

3. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 2, characterized in that: The inner valve stem (4) has a T-shaped longitudinal section along its axial direction. The inner valve stem (4) includes a column head (401) for supporting the support spring (9) and a rod body (402) that can abut against the bellows assembly (2). Wherein, the column head (401) is clearance-fitted with the inner wall of the through flow channel (301), the outer diameter of the rod body (402) is smaller than the outer diameter of the column head (401), the distance between the outer wall of the rod body (402) and the inner wall of the through flow channel (301) is greater than the distance between the outer wall of the column head (401) and the inner wall of the through flow channel (301), and a flow groove (4011) with its bottom tangent to the outer wall of the rod body (402) is provided on the column head (401).

4. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 3, characterized in that: The top of the through channel (301) is fixedly fitted with a retaining ring (10) that can be movably sleeved on the outer periphery of the column head (401), and the retaining ring (10) can be pressed against the step shoulder surface (4012) provided on the column head (401) along the elastic force direction of the support spring (9).

5. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 1, characterized in that: The electromagnetic drive assembly further includes a moving iron core (11) sleeved around the outer periphery of the top rod (6), a guide sleeve (12) movably covered around the outer periphery of the moving iron core (11) and sleeved around the outer periphery of the fixed iron core (7), a housing (13) covered around the outer periphery of the guide sleeve (12), and an electromagnetic coil (14) embedded between the housing (13) and the guide sleeve (12). The moving iron core (11) is fitted with the inner wall of the guide sleeve (12) with a clearance, the opening end of the housing (13) is sealed and sleeved to the end opening of the valve body (1), and a sealing ring (15) is provided between the guide sleeve (12) and the housing (13).

6. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 5, characterized in that: A sealed cavity is formed between the guide sleeve (12) and the fixed iron core (7), and a gap is reserved between the top rod (6) and the fixed iron core (7) for connecting the sealed cavity and the through cavity.

7. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 5, characterized in that: The outer periphery of the housing (13) and the valve body (1) is provided with several sealing rings (16).

8. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 1, characterized in that: A filter assembly (17) is provided inside the Pd port (106).

9. The variable displacement compressor flow control valve based on valve port adaptive wear compensation according to claim 1, characterized in that: The fixed iron core (7), the top rod (6), the inner valve rod (4), the valve core (3), and the bellows assembly (2) are arranged coaxially.

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