Screw compressor and air conditioner

Abstract

The present disclosure relates to a screw compressor and an air conditioner. The screw compressor comprises a rotor, a body, and a slide valve assembly, the slide valve assembly comprising a slide valve and a slide valve rod, and further comprising a slide valve driving mechanism; the slide valve driving mechanism comprises a driving motor and a driving gear, an outer peripheral wall of the slide valve rod is provided with a driving rack extending along a length direction of the slide valve rod, and the driving gear is in meshing connection with the driving rack; the driving motor is in transmission connection with the driving gear, and is configured to drive the driving gear to rotate, so as to drive the slide valve rod and the slide valve to move along an axis direction of the slide valve rod through the driving rack, so as to adjust a pressure ratio of the compressor.

Description

Technical Field

[0001] This disclosure relates to the field of screw compressor technology, and more particularly to screw compressors and air conditioners. Background Technology

[0002] In refrigeration, air conditioning, and industrial refrigeration, screw compressors are widely used in various refrigeration and heat exchange systems due to their advantages such as stable operation and a wide capacity adjustment range. During the operation of a screw compressor, the loading and unloading of the compressor or the internal volume ratio is usually controlled by adjusting the position of the slide valve, thereby precisely controlling the compressor's pressure ratio to adapt to different operating conditions, such as cooling or heating needs under different ambient temperatures and loads, ensuring the system's heat exchange efficiency and operational stability.

[0003] In existing technologies, screw compressors generally use hydraulic actuation to control the position of the slide valve. Specifically, this control method typically involves a cylinder, an oil piston assembly, and a solenoid valve. By controlling the opening and closing of the solenoid valve, the oil pressure in the cylinder is regulated, switching between high-pressure and low-pressure refrigerant oil. This, in turn, drives the oil piston assembly to move the slide valve along the axis of the compressor body, thereby adjusting the position of the slide valve.

[0004] However, the aforementioned hydraulic drive control structure has several insurmountable drawbacks in practical applications: First, it has extremely high requirements for oil quality. If oil stains or impurities are mixed in the refrigeration oil, it can easily clog the oil circuit or jam the slide valve, leading to poor slide valve movement or even inaccurate control. In severe cases, it can cause mechanical damage to the slide valve or cylinder. Second, the oil control system has a significant risk of leakage. Aging, wear, or assembly errors of the oil circuit seals can all lead to refrigeration oil leakage, which not only reduces the accuracy of oil pressure control and affects the performance of the compressor, but also requires frequent replenishment of refrigeration oil and repair of the sealing structure, significantly increasing maintenance costs. Third, maintenance is difficult. Operations such as cleaning the oil circuit, repairing the solenoid valve, and calibrating the oil pressure in the oil control system all require professional technicians to complete with specialized tools, and the maintenance cycle is long, affecting the continuous operation of the compressor. Fourth, the control accuracy is poor. There is a lag in the transmission of oil pressure, and the on / off control of the solenoid valve is difficult to achieve. The current fine-tuning of hydraulic pressure makes it impossible to precisely position the slide valve, especially in operating conditions where frequent pressure ratio adjustments are required. The slide valve is prone to position drift and cannot stably maintain the target pressure ratio. Fifth, the slide valve is difficult to fix stably. Since hydraulic actuation relies on the balance between the oil pressure and the pressure on both sides of the slide valve to maintain its position, when fluctuations in operating conditions disrupt the pressure balance, the slide valve tends to move back and forth near the target position, further affecting the stability of pressure ratio control. Sixth, energy consumption is high. The hydraulic control system needs to continuously supply high-pressure refrigerant oil to the cylinder, which increases the power consumption of the compressor. Seventh, the pressure ratio adjustment range is limited. Due to the limitations of the oil circuit structure and the control logic of the solenoid valve, the traditional hydraulic pressure control method can only adjust the slide valve to a specific fixed position, corresponding to a specific pressure ratio. It cannot achieve stepless adjustment of the pressure ratio according to changes in operating conditions. If it is necessary to adapt to operating conditions with non-specific pressure ratios, the existing structure cannot meet the requirements for precise control.

[0005] In summary, the existing hydraulically driven slide valve control structure used in screw compressors has significant shortcomings in terms of control accuracy, operational stability, maintenance convenience, and energy consumption control. It is no longer able to meet the current application requirements of refrigeration systems for screw compressors, which demand high precision, high reliability, and low maintenance costs. Therefore, a new slide valve driven control structure is urgently needed to overcome the deficiencies of the existing technology. Utility Model Content

[0006] This disclosure provides a screw compressor and an air conditioner to solve the technical problems of the existing screw compressors, which use a hydraulically driven slide valve control structure and have significant shortcomings in terms of control accuracy, operational stability, maintenance convenience, and energy consumption control.

[0007] The screw compressor provided by the utility model comprises a rotor, a body and a slide valve assembly, wherein the slide valve assembly comprises a slide valve and a slide valve rod. The screw compressor further comprises a slide valve driving mechanism, the slide valve driving mechanism comprises a driving motor and a driving gear, a driving rack extending along the length direction of the slide valve rod is arranged on the outer peripheral wall of the slide valve rod, and the driving gear is meshed with the driving rack. The driving motor is in transmission connection with the driving gear, and is configured to drive the driving gear to rotate, so that the slide valve rod and the slide valve are driven by the driving rack to move along the axial direction of the slide valve rod, thereby adjusting the pressure ratio of the compressor.

[0008] Wherein, the driving motor is a servo motor, and an output shaft of the servo motor is connected with the driving gear, and is configured to directly drive the rotation angle of the driving gear.

[0009] Wherein, the screw compressor further comprises a differential pressure sensor; the differential pressure sensor comprises a first pressure sensor and a second pressure sensor, the first pressure sensor is mounted at a position of the body close to a suction end of the compressor, and is configured to detect a suction pressure P1 on one side of the slide valve; the second pressure sensor is mounted at a position of the body close to a discharge end of the compressor, and is configured to detect a discharge pressure P2 on the other side of the slide valve; start, stop and forward / reverse rotation direction of the driving motor are controlled according to a difference value between P2 and P1.

[0010] Wherein, the screw compressor further comprises a first electromagnetic relay and a second electromagnetic relay, the differential pressure sensor is electrically connected with the first electromagnetic relay and the second electromagnetic relay respectively, the first electromagnetic relay and the second electromagnetic relay are both electrically connected with the driving motor, and the first electromagnetic relay and the second electromagnetic relay serve as signal conversion and circuit control elements between the differential pressure sensor and the driving motor.

[0011] Wherein, a target differential pressure a matched with working conditions of the compressor is preset in the differential pressure sensor; when P2-P1>a, the differential pressure sensor outputs a first control signal to control the first electromagnetic relay to be powered on and the second electromagnetic relay to be powered off, the driving motor rotates forward under the circuit control of the first electromagnetic relay, and drives the slide valve to move towards the suction end of the compressor; when P2-P1<a, the differential pressure sensor outputs a second control signal to control the first electromagnetic relay to be powered off and the second electromagnetic relay to be powered on, the driving motor rotates reversely under the circuit control of the second electromagnetic relay, and drives the slide valve to move towards the discharge end of the compressor; when P2-P1=a, the differential pressure sensor outputs a third control signal to control both the first electromagnetic relay and the second electromagnetic relay to be powered off, and the driving motor stops due to circuit disconnection.

[0012] Wherein, one end of the slide valve rod is connected to the middle of the slide valve, the drive rack is continuously arranged along the length direction of the slide valve rod, and the tooth pitch of the drive rack is adapted to the tooth pitch of the drive gear.

[0013] The slide valve drive mechanism is built into the internal cavity of the machine body, the drive motor is connected to the inner wall of the machine body through a bracket, the drive gear is located on one side of the slide valve rod, and the axis of the drive gear is perpendicular to the axis of the slide valve rod.

[0014] The screw compressor further includes an electromagnetic clamp, which is configured to generate friction between itself and the slide valve rod under magnetic drive. The friction is used to prevent the slide valve rod from continuing to rotate.

[0015] The electromagnetic clamp includes a clamp frame, a coil, an iron core, and at least two clamping rods. The clamp frame is connected to the inner wall of the machine body, and the coil and the iron core are both installed in the middle of the clamp frame. The clamping rods are slidably connected to the clamp frame through a guide structure, with one end of the clamping rod facing the slide valve rod and equipped with a rubber clamp, and the other end facing the iron core. When the coil is energized, the iron core generates magnetism and attracts the clamping rods to move, so that the rubber clamps press against the slide valve rod to limit the position of the slide valve.

[0016] When the coil is de-energized, the clamping rod disengages from the iron core and resets, thereby releasing the slide valve rod.

[0017] The electromagnetic clamp further includes a spring, which is sleeved on the outer periphery of the clamping rod, with one end of the spring abutting against the clamping frame and the other end abutting against the middle of the clamping rod; the spring is used to provide a reset force when the coil is de-energized, so as to move the clamping rod away from the slide valve rod.

[0018] The electromagnetic clamp is electrically linked to the drive motor; when the drive motor stops operating according to the signal from the differential pressure sensor, the coil is synchronously energized; when the drive motor starts operating according to the signal from the differential pressure sensor, the coil is synchronously de-energized.

[0019] The valve stem is provided with multiple clamping rods, each clamping rod is symmetrically distributed around the outer periphery of the valve stem, and the rubber clamp of each clamping rod is adapted to the outer peripheral wall of the valve stem.

[0020] This utility model also provides an air conditioner, including the aforementioned screw compressor.

[0021] Compared with the prior art, the technical solutions provided in this disclosure have the following advantages: The screw compressor and air conditioner provided in this disclosure, compared to traditional hydraulic control which relies on oil circuits, solenoid valves, and oil piston assemblies, employ a purely mechanical meshing transmission. This eliminates the need for oil circuits and related sealing structures, fundamentally avoiding the problem of valve jamming due to oil contamination. It also completely eliminates the risk of oil leakage and eliminates the need for periodic oil circuit cleaning, solenoid valve maintenance, or refrigerant oil replenishment. This significantly reduces the compressor's maintenance difficulty and cost, and also reduces the additional energy consumption caused by continuous oil supply. Furthermore, the meshing transmission between the drive gear and the drive rack on the valve stem has high-precision transmission characteristics, which, combined with the drive motor... Precise control of the rotation process enables the slide valve rod and slide valve to move stably and accurately along the axial direction. This effectively solves the problems of difficult-to-precise positioning of the slide valve and easy drifting near the target position caused by the lag in oil pressure transmission and low oil pressure adjustment accuracy in traditional oil pressure control. Moreover, it is not limited by the constraints of the oil circuit structure on the movement range of the slide valve. By controlling the rotation angle of the drive motor, the slide valve can be flexibly adjusted to any desired position, realizing flexible adjustment of the compressor pressure ratio, rather than traditional oil pressure which can only adapt to a specific fixed pressure ratio. This allows for better adaptation to different working conditions and ensures the operating stability and heat exchange efficiency of the compressor under various working conditions. Attached Figure Description

[0022] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with the present invention and, together with the description, serve to explain the principles of the present invention.

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

[0024] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements in the drawings that include the same reference numerals are designated as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0025] Figure 1 A schematic cross-sectional view of a screw compressor provided in an embodiment of this disclosure; Figure 2 This is a schematic diagram of the electromagnetic clamp in a screw compressor provided in an embodiment of the present disclosure; Figure 3 A simplified diagram of a motor control circuit provided in an embodiment of this disclosure.

[0026] Explanation of reference numerals in the attached figures: 1. Compressor; 11. Rotor; 12. Body; 13. Slide valve assembly; 131. Slide valve; 132. Slide valve rod; 14. Slide valve drive mechanism; 141. Drive motor; 142. Drive gear; 143. Drive rack; 15. Differential pressure sensor; 151. First pressure sensor; 152. Second pressure sensor; 16. First electromagnetic relay; 17. Second electromagnetic relay; 18. Electromagnetic clamp; 181. Clamp frame; 182. Coil; 183. Iron core; 184. Clamping rod; 185. Guide structure; 186. Rubber chuck; 187. Spring; 188. Sleeve. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this disclosure. Based on the embodiments of this disclosure, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this disclosure.

[0028] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed.

[0029] For ease of description, spatial relative terms may be used in the text to describe the relative position or movement of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "front," "back," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure undergoes a positional flip, orientation change, or change of motion, these directional indications will change accordingly. For instance, an element described as "below other elements or features" or "below other elements or features" will subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0030] refer to Figures 1-3 The screw compressor 1 provided in this embodiment includes a rotor 11, a body 12, and a slide valve assembly 13. The slide valve assembly 13 includes a slide valve 131 and a slide valve rod 132. The screw compressor 1 also includes a slide valve drive mechanism 14, which includes a drive motor 141 and a drive gear 142. A drive rack 143 extending along the length direction is provided on the outer peripheral wall of the slide valve rod 132. The drive gear 142 is meshed with the drive rack 143. The drive motor 141 is driven by the drive gear 142 and is used to drive the drive gear 142 to rotate, so as to drive the slide valve rod 132 and the slide valve 131 to move along the axial direction of the slide valve rod 132 through the drive rack 143, so as to adjust the pressure ratio of the compressor 1.

[0031] When compressor 1 needs to adjust the pressure ratio according to the operating conditions, the slide valve drive mechanism 14 realizes power transmission and action execution according to the following logic: After receiving the control signal, the drive motor 141 starts and transmits power to the drive gear 142 connected to it, causing the drive gear 142 to rotate around its own axis. Since the drive gear 142 is meshed with the drive rack 143 extending along the length direction on the outer peripheral wall of the slide valve rod 132, the rotational motion of the drive gear 142 can be directly converted into the linear motion of the drive rack 143, thereby pulling the slide valve rod 132 to move along its axial direction. The connection between the slide valve 131 and the slide valve rod 132 is, for example, a fixed connection or a detachable fixed connection. The slide valve 131 will move synchronously with the slide valve rod 132 along the axial direction inside the machine body 12. By changing the working volume between the rotor 11 and the machine body 12 or the flow path of the airflow in the machine body 12, the pressure ratio of the compressor 1 is finally adjusted. The whole process relies entirely on the mechanical meshing structure to transmit power, without the need for oil circuit medium or additional oil control components.

[0032] Compared to traditional hydraulic control that relies on oil circuits, solenoid valves, and oil piston assemblies, this solution uses pure mechanical meshing transmission, eliminating the need for oil circuits and related sealing structures. This fundamentally avoids the problem of valve 131 jamming due to oil contamination, completely eliminates the risk of oil leakage, and eliminates the need for regular cleaning of the oil circuit, maintenance of the solenoid valve, or replenishment of refrigerant oil. This significantly reduces the maintenance difficulty and cost of compressor 1, and also reduces the additional energy consumption caused by continuous oil supply. Furthermore, the meshing transmission between the drive gear 142 and the drive rack 143 on the valve stem 132 has high-precision transmission characteristics, which, combined with the precise control of the rotation process by the drive motor 141, enables… It can drive the slide valve rod 132 and slide valve 131 to move stably and accurately along the axial direction, effectively solving the problem that the position of slide valve 131 is difficult to accurately locate and easily drifts near the target position due to the lag in oil pressure transmission and low oil pressure adjustment accuracy in traditional oil pressure control. Moreover, it is not limited by the oil circuit structure to restrict the movement range of slide valve 131. By controlling the rotation angle of drive motor 141, slide valve 131 can be flexibly adjusted to any required position, realizing flexible adjustment of the pressure ratio of compressor 1, rather than traditional oil pressure which can only adapt to a specific fixed pressure ratio. This allows it to better adapt to different working conditions and ensure the operating stability and heat exchange efficiency of compressor 1 under various working conditions.

[0033] Considering the specific drive type of the drive motor 141, in the screw compressor 1 provided in this embodiment, the drive motor 141 is a servo motor, and the output shaft of the servo motor is connected to the drive gear 142 to directly drive the rotation angle of the drive gear 142.

[0034] In this way, the servo motor receives the pressure ratio adjustment command from the compressor 1 control system. Based on the high-precision angle control characteristics of the servo motor itself, its output shaft will start and rotate according to the preset rotation angle of the command. Since the output shaft of the servo motor is directly connected to the drive gear 142, the rotation of the output shaft will directly drive the drive gear 142 to rotate synchronously around its own axis, avoiding power loss or lag in the intermediate transmission link. Since the drive gear 142 is meshed with the drive rack 143 extending along the length direction on the outer peripheral wall of the slide valve rod 132, the precise rotation of the drive gear 142 will be converted into the linear motion of the drive rack 143, which will then pull the slide valve rod 132 to move along its axial direction. The slide valve 131 is fixedly connected to the slide valve rod 132 and will move synchronously with the precise linear displacement of the slide valve rod 132. By changing the working volume between the rotor 11 and the body 12 or the flow path of the airflow in the body 12, the precise adjustment of the pressure ratio of the compressor 1 is finally achieved.

[0035] Throughout the process, the servo motor directly drives the drive gear 142 through its output shaft. Combined with its high-precision angle control capability, it ensures the accuracy of the rotation angle of the drive gear 142. Furthermore, through the meshing transmission of the gear and rack, it ensures the accuracy of the displacement of the slide valve rod 132 and the slide valve 131, providing the basis for the precise adjustment of the pressure ratio of the compressor 1 in terms of power transmission and action execution.

[0036] Considering the forward and reverse rotation control scheme of the drive motor 141, the screw compressor 1 provided in this embodiment of the present disclosure also includes a differential pressure sensor 15; the differential pressure sensor 15 includes a first pressure sensor 151 and a second pressure sensor 152. The first pressure sensor 151 is installed on the body 12 near the suction end of the compressor 1 and is used to detect the suction pressure P1 on one side of the slide valve 131; the second pressure sensor 152 is installed on the body 12 near the discharge end of the compressor 1 and is used to detect the discharge pressure P2 on the other side of the slide valve 131; the start, stop and forward / reverse rotation direction of the drive motor 141 are controlled according to the difference between P2 and P1.

[0037] In this way, the start, stop, and forward / reverse direction of the drive motor 141 can be automatically controlled by automatically acquiring the exhaust pressure, thus improving the efficiency of the entire process and avoiding all the problems associated with using a hydraulic drive control structure.

[0038] Considering the specific control scheme between the differential pressure sensor 15 and the drive motor 141, the screw compressor 1 provided in this embodiment of the present disclosure also includes a first electromagnetic relay 16 and a second electromagnetic relay 17. The differential pressure sensor 15 is electrically connected to the first electromagnetic relay 16 and the second electromagnetic relay 17 respectively. The first electromagnetic relay 16 and the second electromagnetic relay 17 are both electrically connected to the drive motor 141. The first electromagnetic relay 16 and the second electromagnetic relay 17 are used as signal conversion and circuit control elements between the differential pressure sensor 15 and the drive motor 141.

[0039] In this way, when the compressor 1 operates, the first pressure sensor 151 installed at the suction end of the body 12 detects the suction pressure P1 on one side of the slide valve 131 in real time, and the second pressure sensor 152 installed at the discharge end of the body 12 detects the discharge pressure P2 on the other side of the slide valve 131 in real time, and synchronously transmits the P1 and P2 signals to the differential pressure sensor 15; the differential pressure sensor 15 calculates the actual differential pressure between P2 and P1 (P2-P1), compares it with the target differential pressure a corresponding to the current working condition of the compressor 1, and then outputs corresponding control signals to the first electromagnetic relay 16 and the second electromagnetic relay 17 according to the comparison result; the signal conversion and circuit control between the differential pressure sensor 15 and the driving motor 141 are realized through the first electromagnetic relay 16 and the second electromagnetic relay 17, which can solve the problems of poor control precision and response lag of the traditional oil pressure-controlled slide valve 131. Specifically, the relay can quickly convert the differential pressure signal into a circuit control command, avoid the lag of oil pressure transmission, ensure timely response of start-stop and forward / reverse rotation of the driving motor 141, thereby realize accurate adjustment of the position of the slide valve 131 and the pressure ratio, and prevent the slide valve 131 from drifting.

[0040] This solution inherits the mechanical transmission structure of driving motor 141 plus gear rack, which has the advantages of no oil leakage and low maintenance. It does not need to maintain the oil circuit and solenoid valve like the traditional oil control system, which reduces maintenance difficulty and cost; meanwhile, through the independent control logic of dual relays, the forward rotation circuit and reverse rotation circuit of the driving motor 141 are clearly distinguished, avoiding circuit misoperation, improving the reliability of pressure ratio adjustment, breaking through the limitation that traditional oil pressure can only adapt to specific pressure ratios, and better adapting to the requirements of different working conditions.

[0041] Specifically, the differential pressure sensor 15 is preset with a target differential pressure a that matches the working condition of the compressor 1; When P2-P1>a, the differential pressure sensor 15 outputs a first control signal, controlling the first electromagnetic relay 16 to be energized and the second electromagnetic relay 17 to be de-energized, the driving motor 141 rotates forward under the circuit control of the first electromagnetic relay 16, driving the slide valve 131 to move toward the suction end of the compressor 1; When P2-P1<a, the differential pressure sensor 15 outputs a second control signal, controlling the first electromagnetic relay 16 to be de-energized and the second electromagnetic relay 17 to be energized, the driving motor 141 reverses under the circuit control of the second electromagnetic relay 17, driving the slide valve 131 to move toward the discharge end of the compressor 1; When P2-P1=a, the differential pressure sensor 15 outputs a third control signal, controlling both the first electromagnetic relay 16 and the second electromagnetic relay 17 to be de-energized, and the driving motor 141 stops due to the circuit being disconnected.

[0042] Before compressor 1 starts operating, differential pressure sensor 15 presets a target differential pressure 'a' that matches the current cooling or heating load, ambient temperature, and other operating conditions. During operation, the first pressure sensor 151, installed at the suction end of the unit 12, continuously monitors the suction pressure P1 on one side of the slide valve 131, and the second pressure sensor 152, installed at the discharge end of the unit 12, continuously monitors the discharge pressure P2 on the other side of the slide valve 131. Both P1 and P2 signals are simultaneously transmitted to differential pressure sensor 15. After calculating the actual differential pressure (P2-P1), differential pressure sensor 15 compares it with the preset target differential pressure 'a' and executes the following control logic based on the comparison result: When the actual pressure difference (P2-P1) > the target pressure difference a, the pressure difference sensor 15 outputs a first control signal, which triggers the first electromagnetic relay 16 to be energized and the second electromagnetic relay 17 to remain de-energized. After the first electromagnetic relay 16 is energized, the forward rotation circuit of the drive motor 141 is activated, and the drive motor 141 rotates forward accordingly. Through the meshing transmission between the drive gear 142 and the drive rack 143 on the outer periphery of the slide valve rod 132, the slide valve rod 132 and the slide valve 131 are driven to move towards the suction end of the compressor 1 to adjust the internal working volume or airflow path of the compressor 1 and reduce the pressure ratio. When the actual pressure difference (P2-P1) is less than the target pressure difference a, the pressure difference sensor 15 outputs a second control signal, which triggers the first electromagnetic relay 16 to de-energize and the second electromagnetic relay 17 to energize. After the second electromagnetic relay 17 is energized, the reverse circuit of the drive motor 141 is activated, and the drive motor 141 reverses accordingly. Similarly, through the gear and rack meshing transmission, it drives the slide valve rod 132 and the slide valve 131 to move towards the exhaust end of the compressor 1 to adjust the working volume or airflow path and increase the pressure ratio. When the actual pressure difference (P2-P1) equals the target pressure difference a, the pressure difference sensor 15 outputs a third control signal. This signal triggers the first electromagnetic relay 16 and the second electromagnetic relay 17 to be de-energized. The drive motor 141 stops running because the power supply circuit is disconnected. The position of the slide valve 131 remains stable, ensuring that the compressor 1 continues to operate at a pressure ratio adapted to the current operating conditions.

[0043] In this way, by preset the target pressure difference 'a' corresponding to the working condition, and by combining the actual pressure difference with 'a' in real time, the circuit state is quickly switched by the help of dual electromagnetic relays, so that the drive motor 141 can rotate forward and backward and stop in a timely manner. This avoids the position drift of the slide valve 131 caused by the lag in traditional oil pressure transmission, and can adjust the target pressure difference 'a' according to different working conditions. This breaks through the limitation that traditional oil pressure can only be adapted to a specific pressure ratio, and achieves precise matching between pressure ratio and working condition.

[0044] Furthermore, without relying on oil circuits, solenoid valves, and oil piston assemblies, it continues the advantages of mechanical transmission using a drive motor 141 combined with gears and racks, eliminating the risk of oil leakage and oil contamination. It eliminates the need for regular oil circuit cleaning, solenoid valve maintenance, or refrigerant oil replenishment, significantly reducing maintenance difficulty and costs, while also minimizing the additional energy consumption from continuous oil supply. Additionally, the dual electromagnetic relays independently control the forward and reverse circuits of the drive motor 141, with clear logic and no interference, preventing abnormal movement of the slide valve 131 due to circuit malfunctions. When the actual pressure difference matches the target pressure difference a, the drive motor 141 immediately stops, ensuring the stable position of the slide valve 131 and further guaranteeing the reliability and heat exchange efficiency of the compressor 1 under various operating conditions.

[0045] Considering the specific linkage scheme between the slide valve rod 132 and the drive rack 143, in the screw compressor 1 provided in this embodiment, one end of the slide valve rod 132 is connected to the middle of the slide valve 131, the drive rack 143 is continuously arranged along the length direction of the slide valve rod 132, and the tooth pitch of the drive rack 143 is adapted to the tooth pitch of the drive gear 142.

[0046] When the compressor 1 needs to adjust the pressure ratio, the drive motor 141 drives the drive gear 142 connected to it to rotate. Since the drive rack 143 is continuously arranged along the length of the slide valve rod 132, and the tooth pitch of the drive rack 143 is matched with the tooth pitch of the drive gear 142, the rotational motion of the drive gear 142 can be precisely converted into the linear motion of the drive rack 143 through inter-tooth meshing, thereby driving the slide valve rod 132 to move smoothly along its axial direction. Since one end of the slide valve rod 132 is connected to the middle of the slide valve 131, the linear motion of the slide valve rod 132 can be synchronously transmitted to the slide valve 131, so that the slide valve 131 moves smoothly along the internal axial direction of the machine body 12. The entire linkage process transmits power through the precise meshing of the drive gear 142 and the drive rack 143, and then the uniform transmission of force is achieved by the connection between the slide valve rod 132 and the middle of the slide valve 131. Finally, the displacement of the slide valve 131 adjusts the internal working volume or airflow path of the compressor 1, thereby completing the pressure ratio adjustment.

[0047] In this way, one end of the valve stem 132 is connected to the middle of the valve stem 131, which can make the valve stem 131 bear force evenly and avoid jamming or displacement deviation caused by force skew when the valve stem 131 moves. This solves the problem of valve stem 131 drifting caused by uneven force on the oil piston in traditional hydraulic drive. At the same time, the drive rack 143 is continuously arranged along the length of the valve stem 132 and is matched with the tooth pitch of the drive gear 142. This can eliminate transmission gap and ensure that the transmission between the drive gear 142 and the drive rack 143 is smooth and without lag or spurring. This achieves precise control of the displacement of the valve stem 131 and breaks through the limitations of traditional hydraulic transmission lag and low adjustment accuracy. This allows for precise adjustment of the pressure ratio of the compressor 1. In addition, the entire linkage structure is a pure mechanical meshing transmission, which does not rely on oil circuits, oil pistons and other components. It continues the advantages of the drive motor 141 combined with the gear rack solution, which has no oil leakage and does not require regular maintenance of the oil circuit. This greatly reduces the maintenance difficulty and cost of the compressor 1 and avoids the impact of oil contamination on the movement of the valve stem 131.

[0048] Considering the specific installation scheme between the drive motor 141, the drive gear 142, and the slide valve rod 132, in the screw compressor 1 provided in this embodiment, the slide valve drive mechanism 14 is built into the internal cavity of the body 12, the drive motor 141 is connected to the inner wall of the body 12 through a bracket, the drive gear 142 is located on one side of the slide valve rod 132, and the axis of the drive gear 142 is perpendicular to the axis of the slide valve rod 132.

[0049] During the operation of compressor 1, the slide valve drive mechanism 14 is built into the internal cavity of the body 12 to avoid interference with external components of the body 12 or other internal components such as the core component of rotor 11; the drive motor 141 is stably connected to the inner wall of the body 12 through a bracket to ensure that the drive motor 141 will not shake or shift during operation, providing a stable foundation for power output. When the pressure ratio needs to be adjusted, the drive motor 141 starts and outputs power, driving the drive gear 142 connected to it to rotate. Since the drive gear 142 is located on one side of the slide valve rod 132, and the axis of the drive gear 142 is perpendicular to the axis of the slide valve rod 132, the rotational motion of the drive gear 142 can be precisely converted into the linear motion of the slide valve rod 132 along its own axis through inter-tooth meshing, thereby driving the slide valve 131 connected to the slide valve rod 132 to move synchronously. By changing the internal working volume or airflow path of the machine body 12, the pressure ratio of the compressor 1 is finally adjusted. The entire power transmission process is stably completed within the internal cavity of the machine body 12, without relying on external structures or oil circuit media.

[0050] In this way, the slide valve drive mechanism 14 is built into the internal cavity of the housing 12, eliminating the need for additional installation space outside the housing 12, saving the overall volume of the compressor 1, avoiding the influence of the external environment on the drive components, and preventing motion interference with core components such as the rotor 11 inside the housing 12, thus improving structural compactness and operational stability. Simultaneously, the drive motor 141 is fixed to the inner wall of the housing 12 by a bracket, which can suppress vibration during motor operation and prevent transmission deviation between the drive gear 142 and the slide valve rod 132 due to motor shaking, solving the problem of oil leakage in traditional hydraulic drives. The piston is prone to displacement accuracy issues due to vibration, which further ensures the accuracy of the slide valve 131's displacement. In addition, the perpendicular arrangement of the drive gear 142 to the axis of the slide valve rod 132 ensures uniform meshing depth and high transmission efficiency between the gear and the drive rack 143 on the slide valve rod 132, eliminating the risk of transmission gaps or jamming. Compared with the lag of traditional hydraulic transmission, it can achieve slide valve 131 position adjustment more quickly and accurately. Moreover, the entire mechanical structure does not rely on the oil circuit, completely eliminating the risk of oil leakage and eliminating the need for regular maintenance of oil circuit components, significantly reducing maintenance difficulty and cost.

[0051] In view of the solution to stop the rotation of the slide valve stem 132 in time, the screw compressor 1 provided in the embodiment of this disclosure further includes an electromagnetic clamp 18. The electromagnetic clamp 18 is configured to generate friction between itself and the slide valve stem 132 under magnetic drive. The friction is used to prevent the slide valve stem 132 from continuing to rotate.

[0052] In this way, by triggering friction to block the valve rod 132 through electromagnetic drive, the inertial movement of the valve rod 132 can be quickly counteracted, preventing the valve rod 131 from deviating from the target position due to inertia after the drive motor 141 stops. This solves the problem of the valve rod 131 being difficult to fix stably in traditional hydraulic control, ensuring the accuracy of pressure ratio adjustment. At the same time, the electromagnetic clamp 18 has a fast response speed and can be triggered synchronously with the stopping action of the drive motor 141. Compared with the lag of traditional hydraulic control, it can fix the position of the valve rod 131 more promptly.

[0053] Considering the specific composition of the electromagnetic clamp 18, in the screw compressor 1 provided in this embodiment, the electromagnetic clamp 18 includes a clamp frame 181, a coil 182, an iron core 183, and at least two clamping rods 184. The clamp frame 181 is connected to the inner wall of the machine body 12, and the coil 182 and the iron core 183 are both installed in the middle of the clamp frame 181. The clamping rods 184 are slidably connected to the clamp frame 181 through a guide structure 185, and one end of the clamping rod 184 is set towards the slide valve rod 132 and is equipped with a rubber clamp 186, while the other end is opposite to the iron core 183. When the coil 182 is energized, the iron core 183 generates magnetism and attracts the clamping rod 184 to move, so that the rubber clamp 186 presses against the slide valve rod 132 to limit the position of the slide valve 131.

[0054] The components of the electromagnetic clamp 18 are first assembled into a stable structure through a preset installation method: the clamp frame 181 is fixedly connected to the inner wall of the machine body 12, providing an installation base for the entire clamp; the coil 182 and the iron core 183 are both assembled in the middle of the clamp frame 181 to ensure a stable magnetic transmission path; at least two clamping rods 184 are slidably mounted on the clamp frame 181 through the guide structure 185, which not only limits the movement direction of the clamping rods 184, but also ensures that they slide smoothly. The rubber clamp 186 at one end of the clamping rod 184 is set towards the slide valve rod 132, and the other end is opposite to the iron core 183, forming a transmission path of the iron core 183, clamping rod 184, and slide valve rod 132.

[0055] When the compressor 1 needs to fix the position of the slide valve 131, such as when the drive motor 141 stops to prevent the slide valve 131 from drifting due to inertia, the coil 182 is energized to generate current. Under the action of the current, the iron core 183 generates magnetism. The magnetic attraction acts on the end of the clamping rod 184 facing the iron core 183, causing the clamping rod 184 to slide along the guide structure 185 towards the iron core 183. During the sliding process of the clamping rod 184, the rubber clamp 186 at the other end of it simultaneously approaches the slide valve rod 132 and finally abuts against the outer peripheral wall of the slide valve rod 132. Through the rubber clamp 186 and the... The friction between the valve stems 132 restricts the movement of the valve stems 132, thereby limiting the position of the valve 131 connected to the valve stems 132 and preventing the valve 131 from deviating from the target position. When it is necessary to release the valve 131 and readjust the pressure ratio, the coil 182 is de-energized, the iron core 183 loses its magnetism, the clamp 184 loses its magnetic attraction and no longer applies a clamping force to the valve stem 132. The rubber clamp 186 disengages from the valve stem 132, and the valve stem 132 can move normally along the axis under the drive of the drive motor 141 without affecting the pressure ratio adjustment action.

[0056] In this way, by using at least two clamping rods 184 to press against the valve stem 132 from different directions, combined with the friction between the rubber clamps 186 and the valve stem 132, a fixing force can be applied evenly, preventing the valve stem 131 from tilting due to unilateral force. This avoids the problem of the valve stem 131 easily moving back and forth near the target position in traditional hydraulic control, significantly improving the stability of the valve stem 131 and ensuring accurate pressure ratio maintenance. The clamping rods 184 are equipped with rubber clamps 186. The rubber material can ensure sufficient friction to prevent the valve stem 132 from moving, while also preventing metal from moving. The mechanical wear caused by the direct contact between the chuck and the valve stem 132 extends the service life of the valve stem 132 and the clamping rod 184, solving the problem of component wear that may be caused by traditional mechanical fixing. Furthermore, the clamping rod 184 is slidably connected to the fixture frame 181 through the guide structure 185. The guide structure 185 can limit the movement trajectory of the clamping rod 184, preventing the clamping rod 184 from deviating during sliding, which would cause the rubber chuck 186 to fail to accurately press against the valve stem 132, ensuring the accuracy of the fixture's operation and further guaranteeing the reliability of the valve stem 131's position fixation.

[0057] In summary, the entire electromagnetic clamp 18 is a purely mechanical and electromagnetic structure that does not rely on oil circuits, oil pistons, or other components. This completely eliminates the risk of clamp failure caused by oil leakage and oil contamination in traditional hydraulic control, and eliminates the need for regular maintenance of oil circuit components, reducing the overall maintenance difficulty of compressor 1. When coil 182 is energized, iron core 183 can quickly generate magnetism, causing clamping rod 184 to immediately press against slide valve rod 132. Compared with the lag in oil pressure transmission in traditional hydraulic control, this can be triggered synchronously with the shutdown action of drive motor 141, promptly preventing slide valve 131 from drifting due to inertia, and further improving the pressure ratio control accuracy.

[0058] For example, the electromagnetic clamp 18 also includes a sleeve 188, which includes a top plate and a lower structure surrounding the top plate. The lower structure of the sleeve 188 is sleeved around the periphery of the entire structure of the iron core 183, coil 182, guide structure 185 and spring 187. The top plate of the sleeve 188 is sleeved around the periphery of the clamping rod 184. The lower structure of the sleeve 188 is connected to the clamp frame 181.

[0059] Considering the impact of de-energizing coil 182 on slide valve stem 132, in the screw compressor 1 provided in this embodiment, when coil 182 is de-energized, clamp rod 184 disengages from the iron core 183 and resets, thereby releasing slide valve stem 132.

[0060] In this way, when the coil 182 is de-energized, the clamp 184 disengages from the iron core 183 and resets to release the slide valve rod 132. This ensures that when the compressor 1 needs to readjust the pressure ratio, if the drive motor 141 restarts according to the pressure difference signal, the slide valve rod 132 will not be continuously constrained by the electromagnetic clamp 18. It can smoothly follow the drive motor 141 to move along the axis through the gear and rack transmission. This avoids the slide valve 131 from being stuck or obstructed due to the clamp not being released in time. This solves the problem that the slide valve 131 may not be able to respond to the adjustment in time due to the residual pressure in the oil circuit when using traditional hydraulic control of the slide valve 131, thus improving the timeliness and smoothness of the pressure ratio adjustment. Secondly, the reset and release of the clamp rod 184 only relies on the disappearance of the magnetic attraction force after the coil 182 is de-energized. No additional manual operation or complex oil circuit depressurization process is required. This avoids the cumbersome steps in traditional oil pressure control that require depressurization through a solenoid valve to release the constraint of the slide valve 131, as well as the risk of incomplete depressurization. At the same time, there is no need to maintain the oil circuit related depressurization components, which further reduces the operational complexity and maintenance cost of the compressor 1 during the adjustment process. This ensures that the slide valve rod 132 can move freely during the adjustment phase to accurately adapt to the pressure ratio requirements of the working conditions.

[0061] Considering the elastic resettable design of the electromagnetic clamp 18, in the screw compressor 1 provided in this embodiment, the electromagnetic clamp 18 further includes a spring 187. The spring 187 is sleeved on the outer periphery of the clamping rod 184, and one end of the spring 187 abuts against the clamp frame 181, and the other end abuts against the middle of the clamping rod 184. The spring 187 is used to provide a reset force when the coil 182 is de-energized, so that the clamping rod 184 moves away from the slide valve rod 132.

[0062] In this way, by sleeved with a spring 187 around the clamping rod 184, and with the two ends of the spring 187 abutting against the clamp frame 181 and the middle of the clamping rod 184 respectively, when the power is off, the spring 187 provides a restoring force to push the clamping rod 184 away from the slide valve rod 132. This ensures that after the power is off, the clamping rod 184 will not experience a delayed or incomplete reset due to its own weight, sliding friction, or other factors. It can reliably disengage from the slide valve rod 132, avoiding the problem that the slide valve rod 132 will be continuously constrained due to the clamping rod 184 failing to move away in time, thus hindering the subsequent drive motor 141 from driving the slide valve 131 to adjust the pressure ratio. Secondly, the structure of the spring 187 sleeved on the outer periphery of the clamping rod 184 and abutting at both ends allows the reset force to act evenly along the axial direction of the clamping rod 184, preventing the clamping rod 184 from deflecting or jamming due to uneven force during reset. This further ensures the stability of the clamping rod 184's reset action and ensures that the slide valve rod 132 is released evenly, preventing local friction caused by the deflection of the clamping rod 184 from affecting the subsequent linear movement accuracy of the slide valve rod 132. Simultaneously, the reset of the spring 187 does not require an additional power source or complex oil circuit pressure relief components, continuing the advantage of the electromagnetic clamp 18's oil-free control. Unlike traditional hydraulic systems, it eliminates the need to maintain pressure relief components, reducing the maintenance cost of the compressor 1 and the risk of failure during the adjustment phase.

[0063] Considering the linkage scheme between the electromagnetic clamp 18 and the drive motor 141, in the screw compressor 1 provided in this embodiment, the electromagnetic clamp 18 and the drive motor 141 are electrically linked; when the drive motor 141 stops operating according to the signal of the differential pressure sensor 15, the coil 182 is synchronously energized; when the drive motor 141 starts operating according to the signal of the differential pressure sensor 15, the coil 182 is synchronously de-energized.

[0064] In this way, when the drive motor 141 stops operating according to the signal from the differential pressure sensor 15, the coil 182 is simultaneously energized, enabling the electromagnetic clamp 18 to start immediately and fix the valve stem 132. This instantly counteracts the tendency of the valve stem 132 to move due to inertia, preventing the valve stem 131 from deviating from the target position. This completely solves the problem of easy drifting and difficulty in stable fixing of the valve stem 131 after the motor stops in traditional hydraulic control, ensuring that the pressure ratio of the compressor 1 is always maintained within the accurate range of the suitable working conditions. Furthermore, when the drive motor 141 starts operating according to the signal from the differential pressure sensor 15, the coil 182 is simultaneously de-energized, and the electromagnetic clamp 18 can release the valve stem 132 in time without imposing additional constraints on the movement of the valve stem 132. This ensures that the valve stem 131 can smoothly follow the drive motor 141 to adjust its position through gear and rack transmission, avoiding the situation in traditional hydraulic control where the valve stem 131 may respond late due to residual pressure in the oil circuit. This significantly improves the timeliness and smoothness of pressure ratio adjustment.

[0065] Considering the installation scheme of the clamping rod 184 in the electromagnetic clamp 18, in the screw compressor 1 provided in this embodiment, the number of clamping rods 184 is set to multiple, and each clamping rod 184 is symmetrically distributed on the outer periphery of the slide valve rod 132, and the rubber clamps 186 of each clamping rod 184 are adapted to the outer peripheral wall of the slide valve rod 132.

[0066] In this way, by setting multiple clamping rods 184 and distributing them symmetrically around the outer periphery of the valve stem 132, and by ensuring that the rubber clamps 186 of each clamping rod 184 are adapted to the outer peripheral wall of the valve stem 132, a uniform clamping force can be applied to the valve stem 132. This avoids the problem of unilateral force deviation and unstable fixation of the valve stem 132 caused by a single or asymmetrical distribution of clamping rods 184. This completely solves the core defects of traditional hydraulic control valve 131, which is difficult to fix stably and is prone to drifting near the target position. It ensures that the position of the valve 131 is accurately locked, thereby maintaining the pressure ratio of compressor 1 within the range of suitable operating conditions.

[0067] Meanwhile, the rubber clamps 186 of each clamping rod 184 are adapted to the outer peripheral wall of the valve stem 132, which can increase the contact area between the rubber clamps 186 and the valve stem 132, so that the friction force is evenly applied to the outer peripheral wall of the valve stem 132. This can reliably counteract the movement tendency of the valve stem 132 due to inertia, and also avoid wear on the outer peripheral wall of the valve stem 132 caused by too small contact area and excessive local pressure, thus extending the service life of the valve stem 132 and the clamping rod 184.

[0068] This disclosure also provides an air conditioner, including the aforementioned screw compressor 1, which can achieve all the effects of the screw compressor 1, and will not be described in detail here.

[0069] To better understand the screw compressor 1 and air conditioner solutions provided in this disclosure, the following practical examples are used for further explanation: This disclosure provides a screw compressor 1, which adaptively adjusts the pressure ratio and can fix the position of the slide valve 131 by adjusting its position. The slide valve 131 is adjusted using a rack and pinion drive. A rack is mounted on the slide valve 131, and a servo motor drives a gear 142 to move the slide valve 131. A differential pressure sensor 15 is installed on the slide valve 131 to sense the pressure difference and transmit the feedback to the motor control, thus achieving the adaptive effect. An electromagnetic clamp 18 is also provided, which reacts more quickly than the rack and pinion mechanism and can prevent the slide valve 131 from moving, avoiding the gear continuing to move the slide valve 131 due to inertia when the motor stops. Compared to traditional hydraulic control of the slide valve 131 position, this structure offers higher control precision, prevents the slide valve 131 from moving erratically, and allows for more reliable maintenance. It avoids the problems of poor control precision, complex maintenance, and erratic movement of the slide valve 131 inherent in traditional hydraulic control systems.

[0070] The adjustment structure of the slide valve 131 in a traditional screw compressor generally uses oil pressure to control the movement of the slide valve 131. When the oil in the cylinder is high pressure, the slide valve 131 moves towards the suction end; when the oil in the cylinder is low pressure, the slide valve 131 moves towards the discharge end. The oil pressure is controlled by a solenoid valve switch. This control method has the disadvantages of being difficult to accurately control the position of the slide valve 131, having the risk of leakage, and being difficult to maintain.

[0071] This disclosure provides a screw compressor 1 structure with adaptive control of the slide valve 131 position via a gear and rack mechanism driven by pressure difference. Referring to the accompanying drawings, the compressor 1 mainly consists of three parts: first, a rotor 11 and a housing 12, which is consistent with the structure of a conventional compressor 1; second, a slide valve 131 control part, in which a motor drives a gear to control the position of the slide valve 131, and a rack on the slide valve stem 132 engages with the gear, controlling the forward and reverse rotation and start / stop of the motor to control the displacement of the slide valve 131 through pressure difference; and third, an electromagnetic clamp 18.

[0072] The slide valve 131 is connected to the slide valve rod 132. The slide valve rod 132 is equipped with a rack, which cooperates with a gear driven by a servo motor to control the slide valve rod 132 and thus control the movement of the slide valve 131. This transmission structure is built into the compressor 1, which can effectively save space. Since the compressor 1 no longer controls the position of the slide valve 131 by oil pressure, the oil piston assembly is also eliminated.

[0073] The compressor 1 requires the slide valve 131 to move back and forth during actual operation. Therefore, this structure needs to control the forward and reverse rotation and start and stop of the motor through pressure difference to control the back and forth movement of the slide valve 131.

[0074] Regarding the scheme for precisely controlling the position of slide valve 131 based on the pressure difference of slide valve 131: This structure can adaptively control the position of slide valve 131 by utilizing the pressure difference between its intake and exhaust terminals. A pressure sensor is installed at each end of slide valve 131 to measure the intake and exhaust pressures, P1 and P2 respectively. The pressure difference P2-P1 is calculated, and the corresponding intake and exhaust pressure difference value is 'a', which varies with the operating conditions. The pressure signal is transmitted to the auxiliary... Figure 3 As shown, if P2-P1>a, the first electromagnetic relay 16 operates normally, the second electromagnetic relay 17 is disconnected, the motor rotates forward, and the slide valve 131 moves towards the suction end; if P2-P1<a, the first electromagnetic relay A is disconnected, the second electromagnetic relay 17 operates normally, the motor reverses, and the slide valve 131 moves towards the discharge end; if P2-P1=a, both relays are disconnected, the circuit is broken, the motor stops rotating, and the slide valve 131 stops. Under different operating conditions, the pressure difference of compressor 1 varies. Through the above structure, the position of the slide valve 131 can be adaptively adjusted according to the pressure difference, and the adjustment accuracy is significantly higher than that of oil pressure control.

[0075] When using a rack and pinion drive, there is a possibility that the gears and slide valve 131 may continue to move after the motor stops due to inertia. Therefore, a locking device for slide valve 131 is added. This compressor 1 is equipped with an electromagnetic clamp 18, which acts on the slide valve stem 132. When the motor stops, P2-P1=a, the coil 182 is energized, the iron core 183 becomes magnetic, driving the clamping rods 184 with opposite magnetic properties to move towards the slide valve stem 132. The four clamping rods 184 clamp the slide valve stem 132, and the heads of the clamping rods 184 are fitted with rubber material, using friction to stop and fix the slide valve stem 132. When the motor starts, the coil 182 is no longer energized, the iron core 183 is no longer magnetic, the clamping rods 184 return to their original position, and the slide valve stem 132 can move normally. Because the clamp is electromagnetically driven, its reaction speed is significantly faster, enabling it to quickly act on the start and stop of the movement of the slide valve 131.

[0076] For example, in this embodiment of the present disclosure, a rack and pinion transmission method is used to adaptively control the position of the slide valve 131 according to the pressure difference. Equipped with an electromagnetic clamp 18, the position of the slide valve 131 can be precisely controlled. The current converted from the pressure difference signal controls the on / off state of the electromagnetic relay to control the rotation of the motor, thereby controlling the position of the slide valve 131. The same effect can also be achieved using the following scheme: PLC control is adopted, using differential pressure signals to control the PLC and control circuit, thereby controlling the motor rotation to achieve the same effect.

[0077] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also mean including the plural forms. The terms “comprising,” “including,” “containing,” and “including” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0078] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0079] The above description is merely a specific embodiment of the present invention, enabling those skilled in the art to understand or implement the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A screw compressor, comprising a rotor, a housing, and a slide valve assembly, wherein the slide valve assembly comprises a slide valve and a slide valve stem, characterized in that, The screw compressor further comprises a slide valve driving mechanism; The slide valve driving mechanism comprises a driving motor and a driving gear, a driving rack extending along the length direction of the slide valve rod is arranged on the outer peripheral wall of the slide valve rod, and the driving gear is in meshing connection with the driving rack; the driving motor is in transmission connection with the driving gear and is used for driving the driving gear to rotate, so that the slide valve rod and the slide valve are driven by the driving rack to move along the axial direction of the slide valve rod, so as to adjust the pressure ratio of the compressor.

2. Screw compressor according to claim 1, characterized in that The driving motor is a servo motor, and an output shaft of the servo motor is connected with the driving gear and used for directly driving the rotation angle of the driving gear.

3. Screw compressor according to claim 1, characterized in that The screw compressor further comprises a differential pressure sensor; the differential pressure sensor comprises a first pressure sensor and a second pressure sensor, the first pressure sensor is installed at a position of a compressor body close to a suction end of the compressor and is used for detecting suction pressure P1 on one side of the slide valve; the second pressure sensor is installed at a position of the compressor body close to a discharge end of the compressor and is used for detecting discharge pressure P2 on the other side of the slide valve; starting, stopping and forward / reverse rotation direction of the driving motor are controlled according to a difference value between P2 and P1.

4. Screw compressor according to claim 3, characterized in that The screw compressor further comprises a first electromagnetic relay and a second electromagnetic relay, the differential pressure sensor is electrically connected with the first electromagnetic relay and the second electromagnetic relay respectively, both the first electromagnetic relay and the second electromagnetic relay are electrically connected with the driving motor, and the first electromagnetic relay and the second electromagnetic relay are used as signal conversion and circuit control elements between the differential pressure sensor and the driving motor.

5. Screw compressor according to claim 4, characterized in that A target differential pressure a matched with the working condition of the compressor is preset in the differential pressure sensor; When P2-P1 > a, the differential pressure sensor outputs a first control signal to control the first electromagnetic relay to be powered on and the second electromagnetic relay to be powered off, the driving motor rotates forward under the circuit control of the first electromagnetic relay, and drives the slide valve to move toward the suction end of the compressor; When P2-P1 < a, the differential pressure sensor outputs a second control signal to control the first electromagnetic relay to be powered off and the second electromagnetic relay to be powered on, the driving motor reverses under the circuit control of the second electromagnetic relay, and drives the slide valve to move toward the discharge end of the compressor; When P2-P1 = a, the differential pressure sensor outputs a third control signal to control both the first electromagnetic relay and the second electromagnetic relay to be powered off, and the driving motor stops operating due to circuit disconnection.

6. The screw compressor according to claim 1, characterized in that, One end of the slide valve rod is connected with the middle part of the slide valve, the driving rack is continuously arranged along the length direction of the slide valve rod, and the tooth pitch of the driving rack is adapted to the tooth pitch of the driving gear.

7. The screw compressor according to claim 1, characterized in that, The slide valve driving mechanism is built in an internal cavity of the compressor body, the driving motor is connected to the inner wall of the compressor body through a support, the driving gear is located on one side of the slide valve rod, and the axis of the driving gear is perpendicular to the axis of the slide valve rod.

8. The screw compressor according to claim 3, characterized in that, The screw compressor also includes an electromagnetic clamp configured to generate friction between itself and the valve stem under magnetic drive, the friction being used to prevent the valve stem from continuing to rotate.

9. The screw compressor according to claim 8, characterized in that, The electromagnetic clamp includes a clamp frame, a coil, an iron core, and at least two clamping rods. The clamp frame is connected to the inner wall of the machine body, and the coil and the iron core are both installed in the middle of the clamp frame. The clamping rods are slidably connected to the clamp frame through a guide structure, and one end of the clamping rod is positioned towards the slide valve rod and equipped with a rubber clamp, while the other end is opposite to the iron core. When the coil is energized, the iron core generates magnetism and attracts the clamping rods to move, so that the rubber clamps press against the slide valve rod to limit the position of the slide valve.

10. The screw compressor according to claim 9, characterized in that, When the coil is de-energized, the clamping rod disengages from the iron core and resets, thereby releasing the slide valve rod.

11. The screw compressor according to claim 9, characterized in that, The electromagnetic clamp also includes a spring, which is sleeved on the outer periphery of the clamping rod, with one end of the spring abutting against the clamp frame and the other end abutting against the middle of the clamping rod; the spring is used to provide a reset force when the coil is de-energized, so as to move the clamping rod away from the slide valve rod.

12. The screw compressor according to claim 9, characterized in that, The electromagnetic clamp is electrically linked to the drive motor; when the drive motor stops operating according to the signal from the differential pressure sensor, the coil is synchronously energized; when the drive motor starts operating according to the signal from the differential pressure sensor, the coil is synchronously de-energized.

13. The screw compressor according to claim 9, characterized in that, The number of clamping rods is set to multiple, and each clamping rod is symmetrically distributed on the outer periphery of the slide valve rod, and the rubber clamp of each clamping rod is adapted to the outer peripheral wall of the slide valve rod.

14. An air conditioner, characterized in that, Including the screw compressor as described in any one of claims 1-13.

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