Screw compressor and electric appliance

Abstract

The application relates to a screw compressor and an electrical appliance, the screw compressor comprising a slide valve driving assembly, a rotor assembly and a clutch assembly, the slide valve driving assembly comprising a valve block, a nut and a screw shaft, the valve block being fixedly connected with the nut, the screw shaft having a screw segment matched with the nut; the screw shaft further has an overhanging segment, the overhanging segment being provided with a first driving element, the first driving element being capable of rotating synchronously with the screw shaft; the rotor assembly comprises a main shaft, the main shaft being provided with a second driving element, the second driving element being in transmission connection with the first driving element, and being used for driving the main shaft to rotate through the rotation of the screw shaft; the clutch assembly is connected with the first driving element and / or the second driving element, and is used for removing the transmission between the first driving element and the second driving element. The screw compressor provided by the application can realize the position adjustment of the valve block through the rotation of the screw shaft, and can drive the main shaft to rotate at a low speed, so that the starting current of the screw compressor can be reduced while realizing the precise position adjustment of the valve block.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more particularly to a screw compressor and electrical equipment. Background Technology

[0002] Screw compressors typically consist of a pair of high-precision helical rotors, namely a male rotor and a female rotor. The male rotor is the driving rotor, and the female rotor is the driven rotor. The male and female rotors rotate in opposite directions and mesh. The refrigerant gas is enclosed in the compression chamber between the rotor teeth, and the gas compression is achieved through the periodic change of the volume between the teeth.

[0003] From the reference Figure 1 In existing screw compressors, a rotor 300 and a slide valve assembly 100 are installed inside the casing 400. By moving the slide valve assembly 100 axially along the rotor 300, the effective length of the inter-tooth volume can be changed, achieving stepless adjustment of the output gas volume of the screw compressor. This allows the compressor to dynamically adjust its cooling capacity or discharge volume according to changes in system load. However, in existing technologies, the axial movement of the slide valve assembly 100 is usually achieved through an oil piston assembly 200. This not only has disadvantages such as poor control accuracy and high maintenance costs, but also increases the energy consumption of the screw compressor because the oil piston assembly 200 requires continuous oil supply.

[0004] In addition, when the main motor of the rotor assembly of a traditional screw compressor starts, the rotor assembly is in a stationary state. When the driving rotor changes from a stationary state to a rotating state, a current peak will occur, namely the stall current. The excessively high stall current makes the screw compressor need to be configured with high power and high current power distribution parameters, which not only increases the cost, but also leads to an increase in the energy consumption of the screw compressor. Utility Model Content

[0005] This application provides a screw compressor and electrical equipment to solve the technical problems of high cost and high energy consumption of traditional screw compressors in the prior art.

[0006] In a first aspect, this application provides a screw compressor, comprising:

[0007] A slide valve drive assembly includes a valve block, a nut, and a lead screw shaft. The valve block is fixedly connected to the nut, and the lead screw shaft has a lead screw section that mates with the nut. The lead screw shaft also has an extension section, on which a first drive member is provided. The first drive member can rotate synchronously with the lead screw shaft.

[0008] The rotor assembly includes a main shaft, on which a second driving member is provided. The second driving member is connected to the first driving member for driving the main shaft to rotate through the rotation of the lead screw.

[0009] A clutch assembly is connected to a first drive member and / or a second drive member to disengage the transmission between the first drive member and the second drive member.

[0010] Optionally, the first driving member is coaxially arranged with the cantilever section, and the first driving member is slidably arranged on the cantilever section, and at least part of the cross section of the cantilever section is a non-circular cross section; the clutch assembly is connected to the first driving member, driving the first driving member to slide axially in the cantilever section.

[0011] Optionally, the second drive member is coaxially arranged with the main shaft, and the second drive member is slidably arranged on the main shaft, and at least part of the cross section of the main shaft is a non-circular cross section; the clutch assembly is connected to the second drive member, driving the second drive member to slide axially on the main shaft.

[0012] Optionally, both the first driving component and the second driving component are spur gears.

[0013] Optionally, the clutch assembly includes a cylinder, a piston, and a connecting member. The piston is slidably disposed inside the cylinder, dividing the inside of the cylinder into a first chamber and a second chamber. The piston is driven to slide inside the cylinder by the pressure difference between the first chamber and the second chamber.

[0014] One end of the connector is connected to the piston, and the other end of the connector is connected to the first or second drive member, so that the first or second drive member moves with the piston.

[0015] Optionally, the first chamber is connected to the intake port of the screw compressor, and the second chamber is connected to the exhaust port of the screw compressor.

[0016] Optionally, the connector includes a connecting rod that extends into the cylinder and connects to the piston, with the length direction of the connecting rod parallel to the sliding direction of the piston;

[0017] The cylinder body is provided with a first through hole for passing through the connecting rod, and a first sealing element is provided on the inner wall of the first through hole.

[0018] Optionally, the connector further includes a connecting block, which is rotatably connected to the first driving member;

[0019] Alternatively, the connecting block may be rotatably connected to the second driving component.

[0020] Optionally, the slide valve drive assembly further includes a first bearing assembly and a second bearing assembly, which are respectively disposed at both ends of the lead screw segment.

[0021] Optionally, the screw compressor also includes a housing assembly and a detection assembly. The valve block is disposed inside the housing assembly, and the detection assembly includes an intake pressure sensor and an exhaust pressure sensor disposed inside the housing assembly, which are used to detect the intake pressure and exhaust pressure of the screw compressor, respectively.

[0022] The slide valve drive assembly also includes a rotary drive component, which drives the lead screw shaft to rotate, and both the intake pressure sensor and the exhaust pressure sensor are connected to the rotary drive component for signal transmission.

[0023] Optionally, both the main shaft and the cantilever section extend out of the machine body assembly. The machine body assembly is provided with a second through hole for the main shaft to pass through, and a second seal is provided on the inner wall of the second through hole. The machine body assembly is provided with a third through hole for the cantilever section to pass through, and a third seal is provided on the inner wall of the third through hole.

[0024] Secondly, this application provides an electrical device, including the screw compressor provided in the first aspect of this application.

[0025] The technical solutions provided in this application have the following advantages compared with the prior art:

[0026] The screw compressor provided in this application embodiment achieves precise position adjustment of the valve block through the cooperation of the nut and the lead screw shaft. At the same time, the rotation of the lead screw shaft can drive the main shaft of the first drive component, the second drive component, and the rotor assembly to rotate, so that the main shaft has a certain initial speed, which helps to reduce the peak current of the compressor starting the main shaft rotation. The transmission between the first drive component and the second drive component (i.e., the transmission between the lead screw shaft and the main shaft) can be released through the clutch assembly, avoiding interference with the slide valve position adjustment and rotor rotation during the operation of the screw compressor.

[0027] The electrical equipment provided in this application includes the above-mentioned screw compressor. The cost and energy consumption of the screw compressor can be reduced by setting the slide valve drive component. Therefore, it naturally has the technical effects of the above-mentioned screw compressor. Attached Figure Description

[0028] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0029] To more clearly illustrate the technical solutions in the embodiments of this application 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.

[0030] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0031] Figure 1A cross-sectional view of a screw compressor in the prior art;

[0032] Figure 2 A cross-sectional view of a screw compressor provided in an embodiment of this application;

[0033] Figure 3 This is a schematic diagram of the structure of the lead screw shaft provided in an embodiment of this application;

[0034] Figure 4 A schematic diagram illustrating the cooperation between the first driving component and the second driving component provided in an embodiment of this application;

[0035] Figure 5 This is a schematic diagram of the structure of the first driving component provided in an embodiment of this application;

[0036] Figure 6 A partial cross-sectional view of the clutch assembly provided in an embodiment of this application;

[0037] Figure 7 This is a schematic diagram showing the connection between the connector and the first driving member provided in an embodiment of this application;

[0038] Figure 8 This is a schematic diagram of the structure of the connecting block provided in an embodiment of this application;

[0039] Figure 9 A schematic diagram of the self-locking principle of the slide valve drive assembly provided in the embodiments of this application;

[0040] Figure 10 This is a schematic diagram of the control of the rotary drive component provided in an embodiment of this application.

[0041] Explanation of reference numerals in the attached figures:

[0042] 1. Spool valve drive assembly; 11. Valve block; 12. Nut; 13. Lead screw shaft; 131. Lead screw section; 132. Overhang section; 133. Connecting end; 134. Limiting end; 14. First driving component; 141. Annular groove; 142. Non-circular shaft hole; 143. Gear tooth; 15. First bearing assembly; 16. Second bearing assembly; 17. Rotary driving component; 18. Coupling;

[0043] 2. Rotor assembly; 21. Main shaft; 22. Second drive component;

[0044] 3. Clutch assembly; 31. Cylinder block; 311. First cavity; 312. Second cavity; 313. First through hole; 314. First seal; 315. First connecting pipe; 316. Second connecting pipe; 32. Piston; 33. Connector; 331. Connecting rod; 332. Connecting block; 3321. Connecting arm; 3322. Limiting protrusion; 3323. Fourth through hole; 3324. Clearance groove;

[0045] 4. Body components;

[0046] 5. Detection components; 51. Inhalation pressure sensor; 52. Exhaust pressure sensor;

[0047] 6. Control components; 61. First relay; 62. Second relay;

[0048] 100. Slide valve assembly; 200. Oil piston assembly; 300. Rotor; 400. Housing. Detailed Implementation

[0049] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0050] The following disclosure provides numerous different embodiments or examples for implementing various structures of this application. 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 this application. 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.

[0051] 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.

[0052] To address the high cost and high energy consumption issues of traditional screw compressors in the prior art, this application provides a screw compressor and electrical equipment. The screw compressor achieves precise position adjustment of the valve block 11 through the cooperation of the nut 12 and the lead screw shaft 13. At the same time, the rotation of the lead screw shaft 13 can drive the main shaft 21 of the rotor assembly 2 to rotate, giving the main shaft 21 a certain initial speed, which helps to reduce the peak current of the compressor starting the rotation of the main shaft 21. The clutch assembly 3 can disengage the transmission between the first drive component 14 and the second drive component 22 (i.e., the transmission between the lead screw shaft 13 and the main shaft 21), avoiding interference with the adjustment of the slide valve position and the rotation of the rotor during the operation of the screw compressor.

[0053] Please see Figures 1 to 10 The first aspect of this application provides a screw compressor, including a slide valve drive assembly 1, a rotor assembly 2, and a clutch assembly 3, such as... Figure 2 As shown.

[0054] The slide valve drive assembly 1 includes a valve block 11, a nut 12, and a lead screw shaft 13. The valve block 11 is fixedly connected to the nut 12, allowing the valve block 11 and the nut 12 to move synchronously. The lead screw shaft 13 has a lead screw section 131 that cooperates with the nut 12. By rotating the lead screw shaft 13, the nut 12 can be driven to move on the lead screw section 131, thereby realizing the axial movement of the valve block 11 along the rotor assembly 2, achieving adjustment of the effective length of the inter-tooth volume, and thus realizing stepless adjustment of the output gas volume of the screw compressor.

[0055] The lead screw shaft 13 also has an extension section 132, on which a first driving member 14 is provided. The first driving member 14 can rotate synchronously with the lead screw shaft 13, such as... Figure 2 and Figure 3 As shown.

[0056] The rotor assembly 2 includes a main shaft 21, which transmits the power of the main motor of the screw compressor to the driving rotor (i.e., the male rotor), thereby realizing the reverse rotational meshing between the driving rotor and the driven rotor (i.e., the female rotor), and thus realizing the compression of the refrigerant gas.

[0057] The main shaft 21 is equipped with a second drive component 22, which is connected to the first drive component 14. The rotation of the first drive component 14 drives the rotation of the second drive component 22, so that the power can be transmitted sequentially through the lead screw shaft 13, the first drive component 14, the second drive component 22 and the main shaft 21. Thus, the rotation of the lead screw shaft 13 drives the main shaft 21 to rotate, so that the main shaft 21 has an initial speed before the main motor starts, and the rotor assembly 2 reaches a low-speed rotation state. The main motor starts after the main shaft 21 rotates at low speed. Its starting current is much smaller than the stall current of traditional compressors, which can reduce the cost of electrical control and reduce the energy consumption of screw compressors.

[0058] The clutch assembly 3 is connected to the first drive member 14 and / or the second drive member 22, and can be used to realize the position movement of the first drive member 14 and / or the second drive member 22, so that the relative displacement between the two occurs, thereby disengaging the transmission between the first drive member 14 and the second drive member 22. When the screw compressor is started normally and in a stable working state, it can avoid the connection between the lead screw shaft 13 and the main shaft 21, and avoid mutual interference between the position adjustment of the valve block 11 and the rotation of the rotor assembly 2.

[0059] It should be noted that, compared with the traditional slide valve position adjustment method, this application, through the cooperation of the lead screw shaft 13 and the nut 12, can significantly improve the position control accuracy of the valve block 11, avoiding the risk of oil leakage when the valve block 11 is driven to move by the oil piston assembly. Furthermore, the slide valve drive assembly 1 of this application is relatively easy to maintain. At the same time, through the cooperation of the first drive component 14, the second drive component 22, and the clutch assembly 3, this application can bring the main shaft 21 to a low-speed rotation state before the main motor of the screw compressor starts, which helps to reduce the starting current of the main motor and the energy consumption of the screw compressor. After the main motor starts, the power transmission path between the lead screw shaft 13 and the main shaft 21 can be released through the clutch assembly 3, avoiding mutual interference between the valve block 11 position adjustment and the rotation of the rotor assembly 2 during the operation of the screw compressor.

[0060] In some embodiments of this application, please refer to Figure 2 The valve block 11 and the nut 12 can be separate structures and can be fixed relatively by means of screw connection or welding, or the valve block 11 and the nut 12 can be integrated to reduce the assembly steps of the slide valve drive assembly 1. As long as the valve block 11 can be moved axially in the rotor assembly 2 by the rotation of the lead screw shaft 13, the purpose of this application can be achieved.

[0061] In some embodiments of this application, please refer to Figure 2 , Figure 4 and Figure 5The first driving member 14 is coaxially arranged with the cantilever section 132 and slidably disposed on the cantilever section 132. This allows the first driving member 14 to change its axial position on the cantilever section 132. At least a portion of the cantilever section 132 has a non-circular cross-section, which covers the sliding stroke of the first driving member 14, preventing relative rotation between the first driving member 14 and the cantilever section 132. This allows for both synchronous rotation and relative sliding between the first driving member 14 and the cantilever section 132. The clutch assembly 3 is connected to the first driving member 14, causing it to slide axially along the cantilever section 132. By changing the position of the first driving member 14 relative to the second driving member 22, the transmission connection between the first driving member 14 and the second driving member 22 is switched. This allows power transmission between the first driving member 14 and the second driving member 22 before the main motor starts and disengagement after the main motor starts.

[0062] In other embodiments of this application, the second driving member 22 is coaxially arranged with the main shaft 21 and slidably disposed on the main shaft 21. This allows the second driving member 22 to change its axial position on the main shaft 21. At least a portion of the main shaft 21 has a non-circular cross-section, which covers the sliding stroke of the second driving member 22, preventing relative rotation of the second driving member 22 relative to the main shaft 21. This allows the second driving member 22 and the main shaft 21 to both rotate synchronously and slide relative to each other. The clutch assembly 3 is connected to the second driving member 22, driving the second driving member 22 to slide axially on the main shaft 21. By changing the position of the second driving member 22 relative to the first driving member 14, the transmission connection state between the first driving member 14 and the second driving member 22 is switched. This allows power transmission between the first driving member 14 and the second driving member 22 before the main motor starts and disengagement of the transmission between them after the main motor starts.

[0063] It should be noted that both of the above embodiments can change the relative position between the first driving member 14 and the second driving member 22 through the clutch assembly 3, thereby realizing the switching of the transmission connection state between the first driving member 14 and the second driving member 22. The non-circular cross section can be polygonal, elliptical, elongated, or a combination of multiple shapes. As long as relative rotation between the first driving member 14 and the lead screw shaft 13 and between the second driving member 22 and the main shaft 21 can be prevented, the purpose of this application can be achieved.

[0064] Since the main shaft 21 will change from a low-speed rotation state to a high-speed rotation state after the main motor starts, if the second drive member 22 is slidably mounted on the main shaft 21, it will cause the second drive member 22 to rotate at high speed and produce abnormal noise (due to the gap between the second drive member 22 and the main shaft 21). Therefore, this application preferably fixes the second drive member 22 on the main shaft 21, while the first drive member 14 is slidably mounted on the overhang section 132. The first drive member 14 is provided with a non-circular shaft hole 142 that matches the overhang section 132. The transmission connection state between the first drive member 14 and the second drive member 22 is switched by moving the first drive member 14 through the clutch assembly 3. After the main motor stops, the axial position of the first drive member 14 can be adjusted again by the clutch assembly 3 or by manual adjustment to re-establish the transmission connection with the second drive member 22, so that the main shaft 21 can be pre-set to a low-speed rotation state before the main motor starts again.

[0065] In the above embodiments, the first drive member 14 and the second drive member 22 can be directly connected, or they can be indirectly driven through other components (such as timing belts). However, when the drive member is indirectly driven through other components, the screw compressor will have a complex structure and increased space occupancy. Furthermore, the reliability of the drive member is also poor (for example, after one of the drive members is separated from the timing belt, the timing belt will experience significant shaking and wear on the main shaft 21 and the overhang section 132).

[0066] To avoid the above problems, please refer to some preferred embodiments of this application. Figure 2 , Figure 4 and Figure 5 The first driving member 14 and the second driving member 22 are both spur gears. Power transmission is achieved through direct meshing of the first driving member 14 and the second driving member 22. Since the extension direction of the teeth 143 of the spur gear is parallel to the axial direction of the spur gear, when the clutch assembly 3 drives the spur gear to move along its axial direction to achieve meshing and disengagement, the interference between the two meshing spur gears can be reduced.

[0067] In the above embodiments, the clutch assembly 3 can be any linear actuator, such as a hydraulic cylinder, a pneumatic cylinder, or a linkage mechanism. As long as it can drive the first drive member 14 or the second drive member 22 to move along its axial direction, the purpose of this application can be achieved.

[0068] In some embodiments of this application, please refer to Figure 2 , Figure 6 and Figure 7The clutch assembly 3 includes a cylinder 31, a piston 32, and a connecting member 33. The piston 32 is slidably disposed inside the cylinder 31, dividing the inside of the cylinder 31 into a first chamber 311 and a second chamber 312. The piston 32 is driven to slide inside the cylinder 31 by the pressure difference between the first chamber 311 and the second chamber 312. Specifically, when the internal pressure of the first chamber 311 is greater than the internal pressure of the second chamber 312, the piston 32 moves toward the second chamber 312; when the internal pressure of the first chamber 311 is less than the internal pressure of the second chamber 312, the piston 32 moves toward the first chamber 311.

[0069] One end of the connector 33 is connected to the piston 32 and can move synchronously with the piston 32. The other end of the connector 33 is connected to the first drive member 14 or the second drive member 22, so that the first drive member 14 or the second drive member 22 moves with the piston 32, thereby realizing the relative position change between the first drive member 14 and the second drive member 22, and thus realizing the switching of the transmission connection state between the first drive member 14 and the second drive member 22.

[0070] It should be noted that this application achieves the driving of piston 32 by changing the pressure difference between the first chamber 311 and the second chamber 312, which has the advantages of simple structure and convenient control.

[0071] In some embodiments of this application, please refer to Figure 2 and Figure 6 The first chamber 311 is connected to the intake port of the screw compressor, so that the internal pressure of the first chamber 311 is equal to the intake pressure P1 of the screw compressor. The second chamber 312 is connected to the exhaust port of the screw compressor, so that the internal pressure of the second chamber 312 is equal to the exhaust pressure P2 of the screw compressor.

[0072] Before the main motor starts, the suction pressure P1 of the screw compressor equals the discharge pressure P2, and the piston 32 remains stationary. After the lead screw 13 starts, it drives the first drive member 14 to rotate. The first drive member 14 drives the second drive member 22 and the main shaft 21 to rotate, so that the rotor assembly 2 reaches a low-speed rotation state. At this time, the suction pressure P1 < the discharge pressure P2, that is, the internal pressure of the second chamber 312 is greater than the internal pressure of the first chamber 311. This causes the piston 32 to drive the first drive member 14 or the second drive member 22 to move in the direction of the first chamber 311, so that the first drive member 14 and the second drive member 22 are axially misaligned. After the transmission between the first drive member 14 and the second drive member 22 is released, the main motor starts and drives the main shaft 21 with initial velocity to continue rotating, which can greatly reduce the starting current.

[0073] It should be noted that by connecting the first cavity 311 and the second cavity 312, a linkage relationship can be established between the action of the clutch assembly 3 and the rotation state of the main shaft 21. When the initial rotation speed of the main shaft 21 is sufficient to make the intake pressure P1 < exhaust pressure P2, the clutch assembly 3 can realize the automatic misalignment and separation between the first drive member 14 and the second drive member 22.

[0074] As a specific embodiment of this application, please refer to Figure 6 The first chamber 311 has a first connecting pipe 315 on the side opposite to the piston 32, which is used to connect with the intake port of the screw compressor. The second chamber 312 has a second connecting pipe 316 on the side opposite to the piston 32, which is used to connect with the exhaust port of the screw compressor. The action control of the clutch assembly 3 can be achieved by the change of the intake pressure and exhaust pressure of the screw compressor.

[0075] It is understandable that valves can be installed on the first connecting pipe 315 and the second connecting pipe 316. After the first driving member 14 and the second driving member 22 are separated, the valves can cut off the connection between the first connecting pipe 315 and the intake port and cut off the connection between the second connecting pipe 316 and the exhaust port, so as to prevent the piston 32 from moving again during the normal operation of the screw compressor.

[0076] In some embodiments of this application, please refer to Figure 2 , Figure 6 and Figure 7 The connecting member 33 includes a connecting rod 331, which extends into the cylinder body 31 and connects to the piston 32. The length direction of the connecting rod 331 is parallel to the sliding direction of the piston 32, and the piston 32 can drive the connecting rod 331 to slide along its length direction. The cylinder body 31 is provided with a first through hole 313 for the connecting rod 331 to pass through. The inner wall of the first through hole 313 is provided with a first sealing member 314, which can ensure the airtightness of the cylinder body 31 and prevent leakage risk from the cavity on the piston 32 side (first cavity 311 or second cavity 312) due to the insertion of the connecting rod 331, thus affecting the accuracy of the clutch assembly 3.

[0077] As a specific embodiment of this application, please refer to Figure 2 and Figure 6 The first cavity 311 is located to the left of the piston 32, and the second cavity 312 is located to the right of the piston 32. The connecting rod 331 is inserted into the second cavity 312 and connected to the piston 32. A first through hole 313 and a first sealing element 314 are provided on one side wall of the second cavity 312 to achieve a sealed contact with the connecting rod 331, preventing the insertion of the connecting rod 331 from affecting the sealing performance of the second cavity 312. When the intake pressure P1 < exhaust pressure P2, the piston 32 can drive the connecting rod 331 towards... Figure 6The left side moves, thereby achieving the misalignment and separation of the first driving member 14 and the second driving member 22.

[0078] In some embodiments of this application, please refer to Figure 5 , Figure 7 and Figure 8 The connector 33 also includes a connecting block 332, which is rotatably connected to the first driving member 14 and connected to the connecting rod 331. The connecting rod 331 and the connecting block 332 can drive the first driving member 14 to slide along the axial direction of the cantilever section 132, and the first driving member 14 does not interfere with the rotation of the cantilever section 132.

[0079] In some other embodiments of this application, the connecting block 332 is rotatably connected to the second driving member 22, and the connecting block 332 is connected to the connecting rod 331. The connecting rod 331 and the connecting block 332 can drive the second driving member 22 to slide along the axial direction of the main shaft 21, and there is no interference with the rotation of the main shaft 21 driven by the second driving member 22.

[0080] It should be noted that in both of the above embodiments, the connecting block 332 can be rotatably connected to the first driving member 14 or the second driving member 22 to prevent the connecting block 33 from interfering with the rotation of the first driving member 14 or the second driving member 22.

[0081] As can be seen from the foregoing, this application preferably connects the clutch assembly 3 to the first drive member 14 to achieve the switching of the transmission connection state between the first drive member 14 and the second drive member 22. The following embodiment is described with the connecting block 332 and the first drive member 14 being rotatably connected as an example.

[0082] In some embodiments of this application, when the connecting block 332 is rotatably connected to the first driving member 14, please refer to... Figure 2 , Figure 4 , Figure 5 , Figure 7 and Figure 8 An annular groove 141 is provided on one or both end faces of the first driving member 14. The connecting block 332 is provided with a connecting arm 3321 for connecting with the first driving member 14. The number of connecting arms 3321 can be one or two arranged opposite to each other. The connecting arm 3321 is provided with a limiting protrusion 3322 that cooperates with the annular groove 141. When the first driving member 14 rotates with the cantilever section 132, the limiting protrusion 3322 can be embedded in the annular groove 141 and rotate relative to the annular groove 141. This can achieve the connection between the connecting block 332 and the first driving member 14 while avoiding interference with the rotation of the first driving member 14.

[0083] In some embodiments of this application, please refer to Figure 8The connecting arm 3321 is also provided with a fourth through hole 3323, which can be used to pass through the cantilever section 132 of the lead screw shaft 13. The diameter of the fourth through hole 3323 is larger than the maximum radial dimension of the cantilever section 132 of the first driving member 14, which can prevent the connecting arm 3321 from interfering with the rotation of the cantilever section 132. At the same time, the connecting block 332 is also provided with a relief groove 3324 that matches the first driving member 14, so that part of the first driving member 14 can extend into the relief groove 3324, thus preventing the connecting block 332 from interfering with the rotation of the first driving member 14.

[0084] In some embodiments of this application, please refer to Figure 2 , Figure 3 and Figure 9 The nut 12 and the lead screw section 131 of the lead screw shaft 13 form a ball screw pair. Balls are provided between the nut 12 and the lead screw section 131. The force is transmitted by the rolling of the balls between the lead screw section 131 and the nut 12, realizing the conversion between rotary motion and linear motion. This can reduce friction, improve the transmission efficiency between the lead screw shaft 13 and the nut 12, and help reduce the energy consumption of the slide valve drive assembly 1 and the screw compressor.

[0085] In some embodiments of this application, please refer to Figure 9 The ball screw assembly has a self-locking function, which can keep the valve block 11 stably stopped at the preset position and prevent the valve block 11 from shifting in position relative to the preset position in the axial direction of the rotor assembly 2.

[0086] Specifically, F2 is the supporting force exerted by the ball groove on the ball in the lead screw section 131, F1 is the frictional force exerted by the ball groove on the ball, and F3 is the resultant force of other forces in the vertical direction on the ball (such as the force exerted by the nut 12 on the ball, the weight of the ball itself, etc.). Here, F1 = F2·μ, where μ is the friction coefficient of the ball groove. When F1 > F3·cosα, self-locking can be achieved when the lead screw shaft 13 stops rotating. Therefore, by designing the inclination angle α of the ball groove of the lead screw section 131 relative to the vertical direction, such that 1 / tanα is greater than the friction coefficient μ, the ball screw pair can be guaranteed to have a self-locking function.

[0087] In some embodiments of this application, please refer to Figure 2 The slide valve drive assembly 1 also includes a first bearing assembly 15 and a second bearing assembly 16. The first bearing assembly 15 and the second bearing assembly 16 are respectively disposed at both ends of the lead screw section 131, and can be used to provide rotational support for the lead screw shaft 13, thereby improving the stability and smoothness of the rotation of the lead screw shaft 13.

[0088] In some embodiments of this application, please refer to Figure 2The screw compressor also includes a body assembly 4 and a detection assembly 5. The valve block 11 is disposed inside the body assembly 4. The detection assembly 5 includes a suction pressure sensor 51 and a discharge pressure sensor 52 disposed inside the body assembly 4, which are used to detect the suction pressure P1 and discharge pressure P2 of the screw compressor, respectively.

[0089] The slide valve drive assembly 1 also includes a rotary drive component 17, which is used to drive the lead screw shaft 13 to rotate. The intake pressure sensor 51 and the exhaust pressure sensor 52 are both connected to the rotary drive component 17 to control the rotation of the lead screw shaft 13 according to the pressure difference between the exhaust pressure P2 and the intake pressure P1, thereby achieving adaptive adjustment of the position of the valve block 11 according to the pressure signal.

[0090] In some embodiments of this application, please refer to Figure 2 and Figure 3 The lead screw shaft 13 also includes a connecting end 133 and a limiting end 134. The connecting end 133 can be connected to the rotary drive member 17 via a coupling 18, and the rotary drive member 17 drives the lead screw shaft 13 to rotate. The limiting end 134 is provided with a limiting boss, which can limit the sliding of the first drive member 14 and prevent the first drive member 14 from dislodging from the end of the lead screw shaft 13.

[0091] In some embodiments of this application, please refer to Figure 2 Both the main shaft 21 and the cantilever section 132 extend out of the body assembly 4 to facilitate the placement of the first drive member 14 and the second drive member 22 on the outside of the body assembly 4, thus avoiding any impact on the dimensions of the body assembly 4 caused by the placement of the first drive member 14, the second drive member 22, and the clutch assembly 3. The body assembly 4 has a second through hole for the main shaft 21 to pass through, and a second seal is provided on the inner wall of the second through hole; the body assembly 4 also has a third through hole for the cantilever section 132 to pass through, and a third seal is provided on the inner wall of the third through hole. This ensures the sealing performance of the body assembly 4 and prevents adverse effects on the refrigerant compression process inside the body assembly 4 when the main shaft 21 and the cantilever section 132 extend out of the body assembly 4.

[0092] Please see Figures 1 to 10 The second aspect of this application provides an electrical device including the screw compressor described in the above embodiments. Through this screw compressor, the position of the valve block 11 of the slide valve can be precisely adjusted and self-locked, enabling the screw compressor to dynamically adjust the cooling capacity or discharge volume according to changes in system load, thereby achieving energy saving, optimized operating efficiency, and extended lifespan of the electrical device. Simultaneously, the lead screw 13 in the slide valve drive assembly 1 can drive the main shaft 21 to rotate at low speed, thereby reducing the starting current of the main motor of the screw compressor, which helps to reduce the starting energy consumption of the electrical device and extend its service life.

[0093] It should be noted that the electrical equipment can be air conditioning equipment, refrigeration equipment, heat pump water heating equipment, and other equipment that require refrigerant compression through screw compressors. Because screw compressors have advantages such as compact structure, stable operation, and wide range of applicable operating conditions, they can improve the operational stability of electrical equipment and reduce its energy consumption and maintenance costs.

[0094] Please see Figures 1 to 10 The third aspect of this application provides a control method that uses the screw compressor described in the above embodiments, including the following steps:

[0095] Step 1: Set the preset pressure difference value for each working condition.

[0096] When the operating conditions change, the corresponding optimal intake and exhaust pressure difference also changes. Therefore, it is necessary to set a preset pressure difference for each operating condition to improve the operating efficiency of the screw compressor under any operating condition.

[0097] Step 2: Start the slide valve drive assembly 1. The rotation of the lead screw shaft 13 drives the first drive component 14 to rotate, and the first drive component 14 drives the second drive component 22 and the main shaft 21 to rotate, so that the main shaft 21 has an initial speed. After the main shaft 21 rotates at low speed, the clutch assembly 3 pushes the piston 32 and the connecting component 33 to move by the change of intake pressure P1 and exhaust pressure P2. The connecting component 33 drives the first drive component 14 to slide, realizing the misalignment of the first drive component 14 and the second drive component 22, and releasing the transmission connection between the first drive component 14 and the second drive component 22.

[0098] Step 3: After starting the main motor of the screw compressor, monitor the suction pressure P1 and discharge pressure P2 of the screw compressor;

[0099] Under any operating condition, the pressure difference between the exhaust pressure P2 and the intake pressure P1 is compared with the preset pressure difference value corresponding to that operating condition. Based on the comparison result, the rotation state of the lead screw shaft 13 is controlled to adjust the position of the valve block 11, thereby achieving adaptive adjustment of the position of the valve block 11 of the slide valve through pressure difference changes.

[0100] Specifically, when the exhaust pressure P2 - intake pressure P1 > preset pressure difference a, the control screw shaft 13 rotates forward, causing the valve block 11 to move toward the intake end of the screw compressor, which can reduce the difference between the exhaust pressure P2 and the intake pressure P1, bringing it closer to the preset pressure difference a set under this operating condition.

[0101] When the exhaust pressure P2 - intake pressure P1 < preset pressure difference a, the control screw shaft 13 reverses, causing the valve block 11 to move toward the exhaust end of the screw compressor, which can increase the difference between the exhaust pressure P2 and the intake pressure P1, bringing it closer to the preset pressure difference a set under this operating condition.

[0102] When the exhaust pressure P2 minus the intake pressure P1 equals the preset pressure difference, the control screw shaft 13 stops rotating, causing the valve block 11 to stop moving and maintain the current state, thus ensuring the operating efficiency of the screw compressor.

[0103] In some embodiments of this application, in order to control the rotational state of the lead screw shaft 13, the screw compressor further includes a control component 6. The control component 6 includes a first relay 61 and a second relay 62, and connects the three-phase power supplies L1, L2, and L3 to the UVW terminals of the rotary drive component 17 (i.e., the motor) through the first relay 61 and the second relay 62, respectively. Figure 10 As shown, when the first relay 61 is working normally and the second relay 62 is disconnected, the rotary drive 17 drives the lead screw shaft 13 to rotate forward, causing the valve block 11 to move toward the suction end of the screw compressor; when the first relay 61 is disconnected and the second relay 62 is working normally, the rotary drive 17 drives the valve block 11 to rotate in reverse, causing the valve block 11 to move toward the discharge end of the screw compressor; when both the first relay 61 and the second relay 62 are disconnected, the rotary drive 17 stops working, and the lead screw shaft 13 and the valve block 11 remain stationary.

[0104] In some embodiments of this application, the control component 6 further includes a PLC controller, which can realize intelligent and automated adjustment of the screw compressor.

[0105] The above control method enables the position of valve block 11 to be adaptively adjusted according to the pressure difference, and the adjustment of valve block 11 position can be closely integrated with the working conditions. Compared with the traditional slide valve adjustment method, it can significantly improve the adjustment accuracy and reliability, and reduce maintenance costs and energy consumption.

[0106] 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 include the plural forms. The terms “comprising,” “including,” “containing,” and “having” 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.

[0107] 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.

[0108] The above description is merely a specific embodiment of this application, enabling those skilled in the art to understand or implement this application. 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 this application. Therefore, this application 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 claimed herein.

Claims

1. A screw compressor, characterized in that, include: A slide valve drive assembly (1) includes a valve block (11), a nut (12), and a lead screw shaft (13). The valve block (11) is fixedly connected to the nut (12), and the lead screw shaft (13) has a lead screw section (131) that cooperates with the nut (12). The lead screw shaft (13) also has an extension section (132), and a first drive member (14) is provided on the extension section (132). The first drive member (14) can rotate synchronously with the lead screw shaft (13). The rotor assembly (2) includes a main shaft (21) and a second drive member (22) is provided on the main shaft (21). The second drive member (22) is connected to the first drive member (14) for driving the main shaft (21) to rotate through the rotation of the lead screw shaft (13). A clutch assembly (3) is connected to the first drive member (14) and / or the second drive member (22) to disengage the transmission between the first drive member (14) and the second drive member (22).

2. The screw compressor according to claim 1, characterized in that, The first driving member (14) is coaxially arranged with the cantilever section (132), and the first driving member (14) is slidably arranged on the cantilever section (132). At least part of the cross section of the cantilever section (132) is a non-circular cross section. The clutch assembly (3) is connected to the first driving member (14) and drives the first driving member (14) to slide in the axial direction of the cantilever section (132).

3. The screw compressor according to claim 1, characterized in that, The second drive member (22) is coaxially arranged with the main shaft (21), and the second drive member (22) is slidably arranged on the main shaft (21). At least part of the cross section of the main shaft (21) is a non-circular cross section. The clutch assembly (3) is connected to the second drive member (22) and drives the second drive member (22) to slide in the axial direction of the main shaft (21).

4. The screw compressor according to claim 1, characterized in that, Both the first driving member (14) and the second driving member (22) are spur gears.

5. The screw compressor according to any one of claims 1 to 4, characterized in that, The clutch assembly (3) includes a cylinder (31), a piston (32), and a connector (33). The piston (32) is slidably disposed inside the cylinder (31), dividing the inside of the cylinder (31) into a first chamber (311) and a second chamber (312). The piston (32) is driven to slide inside the cylinder (31) by the pressure difference between the first chamber (311) and the second chamber (312). One end of the connector (33) is connected to the piston (32), and the other end of the connector (33) is connected to the first drive member (14) or the second drive member (22), so that the first drive member (14) or the second drive member (22) moves with the piston (32).

6. The screw compressor according to claim 5, characterized in that, The first cavity (311) is connected to the intake port of the screw compressor, and the second cavity (312) is connected to the exhaust port of the screw compressor.

7. The screw compressor according to claim 5, characterized in that, The connector (33) includes a connecting rod (331), which extends into the interior of the cylinder (31) and connects to the piston (32). The length direction of the connecting rod (331) is parallel to the sliding direction of the piston (32). The cylinder body (31) is provided with a first through hole (313) for the connecting rod (331) to pass through, and a first sealing element (314) is provided on the inner wall of the first through hole (313).

8. The screw compressor according to claim 7, characterized in that, The connector (33) further includes a connecting block (332), which is rotatably connected to the first driving member (14); Alternatively, the connecting block (332) is rotatably connected to the second driving member (22).

9. The screw compressor according to any one of claims 1 to 4, characterized in that, The slide valve drive assembly (1) further includes a first bearing assembly (15) and a second bearing assembly (16), which are respectively disposed at both ends of the lead screw segment (131).

10. The screw compressor according to any one of claims 1 to 4, characterized in that, It also includes a body assembly (4) and a detection assembly (5). The valve block (11) is disposed inside the body assembly (4). The detection assembly (5) includes an intake pressure sensor (51) and an exhaust pressure sensor (52) disposed inside the body assembly (4), which are used to detect the intake pressure and exhaust pressure of the screw compressor, respectively. The slide valve drive assembly (1) further includes a rotary drive (17), which is used to drive the lead screw shaft (13) to rotate, and the intake pressure sensor (51) and the exhaust pressure sensor (52) are both signal connected to the rotary drive (17).

11. The screw compressor according to claim 10, characterized in that, Both the main shaft (21) and the cantilever section (132) extend out of the body assembly (4). The body assembly (4) is provided with a second through hole for the main shaft (21) to pass through, and a second sealing element is provided on the inner wall of the second through hole. The body assembly (4) is provided with a third through hole for the cantilever section (132) to pass through, and a third sealing element is provided on the inner wall of the third through hole.

12. An electrical appliance, characterized in that, Including the screw compressor as described in any one of claims 1 to 11.

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