Coupling design method, system and device for press-insertion tube force and screw tightening torque

Abstract

The application discloses a kind of coupling design method, system and equipment of press insertion pipe force and screw tightening torque, comprising: determine the total fit interference between cylinder insertion pipe and cylinder insertion pipe hole;According to total fit interference, the press insertion pipe force required in press insertion pipe process is obtained by calculation;The maximum value of compressed gas force in pump body assembly is calculated, to determine the friction required between cylinder cover and cylinder end face;Wherein, the minimum value of the friction required between cylinder cover and cylinder end face is greater than the maximum value of the press insertion pipe force required in press insertion pipe process and the maximum value of compressor gas force in pump body assembly;According to the friction required between cylinder cover and cylinder end face, the total pre-tightening force of all screws on cylinder cover is determined, to obtain the pre-tightening force of single screw on cylinder cover, and then the tightening torque of single screw is obtained;The required press insertion pipe force and screw tightening torque coupling design result are determined by the application, to ensure that the air intake passage is sealed well, the pump body radial gap is controllable, and the product performance is effectively improved.

Description

Technical Field

[0001] This invention belongs to the field of compressor design technology, and specifically relates to a coupling design method, system and device for inserting tube force and screw tightening torque. Background Technology

[0002] In existing rotary compressors, an interference fit is made between the cylinder insert 1 and the cylinder insert hole 2 to connect the outlet of the liquid reservoir with the inlet of the cylinder, ensuring the airtightness of the intake airflow channel, as shown in the attached figure. Figure 1-2 As shown; wherein, the cylinder tube is fitted into the tube pressing clamp, and the tube pressing clamp 3 is used to apply the tube pressing force to complete the assembly of the cylinder tube.

[0003] As attached Figure 3 As shown, the cylinder head 4 and the cylinder are generally fastened together by screws 5; wherein, the tightening torque of the screws generates a preload between the end faces of the cylinder head 4 and the cylinder to meet the requirements of rigidity, tightness and anti-loosening ability of the connection of various pump body components.

[0004] During the assembly of cylinder tube 1, the pressing force applied by the pressing tube clamp will generate a lateral load on the cylinder. When the frictional force indirectly generated by the screw tightening torque is insufficient to resist the lateral load, the screw connection will slip, which will cause the minimum radial clearance between the cylinder and the rolling piston in the pump body assembly to change or cause the centering angle of the minimum radial clearance between the cylinder and the rolling piston to change, seriously affecting the product performance of the compressor. Summary of the Invention

[0005] To address the technical problems existing in the prior art, the present invention provides a coupling design method, system, and device for the insertion force and screw tightening torque, in order to solve the problem that when the frictional force indirectly generated by the screw tightening torque is insufficient to resist the lateral load, it will cause the screw connection to slip, which in turn will cause the minimum radial clearance between the cylinder and the rolling piston in the pump body assembly to change or cause the centering angle of the minimum radial clearance between the cylinder and the rolling piston to change, seriously affecting the product performance of the compressor.

[0006] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0007] This invention discloses a coupling design method for insertion force and screw tightening torque, comprising:

[0008] Based on the structural design results of the cylinder insert and cylinder insert hole, determine the total interference fit between the cylinder insert and the cylinder insert hole;

[0009] The pressing force required for the pressing process is calculated based on the total interference fit between the cylinder insertion tube and the cylinder insertion tube hole.

[0010] Based on the structural design results of the cylinder, calculate the maximum value of the compressed gas force in the pump body assembly;

[0011] The frictional force required between the cylinder head and the cylinder end face is determined based on the pressing force required for the pressing process and the maximum value of the compressed gas force in the pump body assembly; wherein, the minimum value of the frictional force required between the cylinder head and the cylinder end face is greater than the maximum value of the pressing force required for the pressing process, and the minimum value of the frictional force required between the cylinder head and the cylinder end face is greater than the maximum value of the compressed gas force in the pump body assembly.

[0012] Determine the total preload of all screws on the cylinder head based on the required friction between the cylinder head and the cylinder end face;

[0013] Based on the total preload of all the screws on the cylinder head, the preload of a single screw on the cylinder head is obtained, and then the tightening torque of the single screw is obtained.

[0014] Furthermore, the total interference fit δ between the cylinder insert and the cylinder insert hole is:

[0015] δ=δ e +3.2(R ao +R ai )

[0016] Wherein, δ is the total interference fit between the cylinder insert and the cylinder insert hole; δ e The calculated value of the total interference fit between the cylinder insert and the cylinder insert hole; R ao R is the surface roughness of the mating surface of the cylinder insert; ai The roughness of the mating surface of the cylinder insertion hole.

[0017] Furthermore, the total interference fit between the cylinder insert and the cylinder insert hole includes a maximum total interference fit and a minimum total interference fit.

[0018] The calculation process for the maximum total interference fit is as follows:

[0019] The maximum value of the total interference fit is obtained based on the difference between the lower deviation of the inner diameter of the cylinder insertion hole and the upper deviation of the outer diameter of the cylinder insertion tube.

[0020] The maximum value of the total interference fit is calculated based on the maximum value of the total interference fit, combined with the surface roughness of the cylinder insert and the surface roughness of the cylinder insert hole.

[0021] The calculation process for the minimum total interference fit is as follows:

[0022] The minimum value of the total interference fit is obtained based on the difference between the upper deviation of the inner diameter of the cylinder insertion hole and the lower deviation of the outer diameter of the cylinder insertion tube.

[0023] The minimum value of the total interference fit is calculated based on the minimum value of the total interference fit, combined with the surface roughness of the cylinder insert and the surface roughness of the cylinder insert hole.

[0024] Furthermore, the minimum total interference fit is greater than 10 μm.

[0025] Furthermore, the force F required for the insertion process is:

[0026] F=Pπd i外 Lμ

[0027]

[0028]

[0029]

[0030] Where, d i内 d is the inner diameter of the cylinder insert; i外 d is the outer diameter of the cylinder insert; o内 d is the diameter of the cylinder insertion hole; o外 The height of the cylinder is μ; the coefficient of friction between the cylinder insert and the cylinder insert hole is E. i E represents the elastic modulus of the cylinder insertion tube. o V is the elastic modulus of the cylinder insertion hole. o V is the Poisson's ratio for cylinder insertion. i C is the Poisson's ratio of the cylinder insertion hole. o C is the stiffness coefficient of the cylinder insertion tube; i This is the stiffness coefficient of the cylinder insertion hole.

[0031] Furthermore, the maximum value of the compressed gas force in the pump assembly is:

[0032] F p =(P d -P s )×H×L

[0033] Among them, F p P is the maximum value of the compressed gas force in the pump assembly; d P is the discharge pressure under the maximum differential pressure condition that the compressor may encounter during operation. s H is the suction pressure under the maximum differential pressure condition that the compressor may encounter during operation; L is the cylinder height; and L is the projected length of the compressed gas acting within the pump body.

[0034] Furthermore, the tightening torque T of a single screw is:

[0035] T = KF o d≥T1+T2

[0036]

[0037]

[0038] f′ min >F p

[0039] f′ min >F

[0040] Where K is the screw tightening factor; d is the nominal diameter of the screw; n is the total number of individual screws on the cylinder head; F o F is the preload force of a single bolt on the cylinder head. n F represents the total number of individual bolts on the cylinder head. p The maximum value of the compressed gas force in the pump body assembly; μ f T1 is the coefficient of friction between the cylinder head and the cylinder mating surface; T2 is the thread resistance torque of the screw thread pair; T3 is the end-face friction torque between the screw end face and the support surface; f′ is the required friction force between the cylinder head and the cylinder end face; f′ min This is the minimum frictional force required between the cylinder head and the cylinder end face.

[0041] This invention also provides a coupling design system for the insertion force and screw tightening torque, comprising:

[0042] The overall assembly interference module is used to determine the total interference fit between the cylinder insert and the cylinder insert hole based on the structural design results of the cylinder insert and cylinder insert hole.

[0043] The insertion force module is used to calculate the insertion force required for the insertion process based on the total interference fit between the cylinder insertion tube and the cylinder insertion tube hole.

[0044] The gas force module is used to calculate the maximum value of the compressed gas force in the pump body assembly based on the structural design results of the cylinder.

[0045] The friction module is used to determine the friction force required between the cylinder head and the cylinder end face based on the pressing force required for the pressing process and the maximum value of the compressed gas force in the pump body assembly; wherein the minimum value of the friction force required between the cylinder head and the cylinder end face is greater than the maximum value of the pressing force required for the pressing process, and the minimum value of the friction force required between the cylinder head and the cylinder end face is greater than the maximum value of the compressed gas force in the pump body assembly;

[0046] The total preload module is used to determine the total preload of all screws on the cylinder head based on the required friction between the cylinder head and the cylinder end face.

[0047] The tightening torque module is used to obtain the preload of a single screw on the cylinder head based on the total preload of all screws on the cylinder head, and then obtain the tightening torque of the single screw.

[0048] This invention also provides a coupling design device for the insertion force and screw tightening torque, comprising:

[0049] Memory, used to store computer programs;

[0050] A processor is used to implement the steps of the coupling design method of the insertion force and screw tightening torque when executing the computer program.

[0051] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0052] This invention provides a coupling design method and system for cylinder insert force and screw tightening torque. Based on the total interference fit between the cylinder insert and the cylinder insert hole, the required insert force is calculated to ensure no working fluid leakage at the cylinder insert interference connection. Based on the required insert force and the maximum compressed gas force in the pump assembly, the required friction force between the cylinder head and the cylinder end face is determined to ensure sufficient friction to resist the lateral load generated during assembly and to overcome the maximum gas compression force during operation. By using quantitative coupling design calculations and selecting the cylinder insert fit dimensions, the required insert force and screw tightening torque coupling design results are determined, ensuring good sealing of the intake channel and controllable radial clearance of the pump body, effectively improving product performance. Attached Figure Description

[0053] Figure 1 This is a schematic diagram of the cylinder tube insertion assembly process;

[0054] Figure 2 This is a partial structural diagram of the cylinder insert and cylinder insert hole;

[0055] Figure 3 This is a schematic diagram of the pump body screw fastening connection;

[0056] Figure 4 This is a flowchart of the coupling design method of the insertion force and screw tightening torque described in this invention.

[0057] The components include: 1. Cylinder insert pipe; 2. Cylinder insert pipe hole; 3. Insert pipe clamp; 4. Cylinder head; 5. Screws. Detailed Implementation

[0058] To make the technical problems solved by the present invention, the technical solutions, and the beneficial effects clearer, the following specific embodiments provide a further detailed description of the present invention. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of the invention.

[0059] As attached Figure 4 As shown, this invention provides a coupling design method for the insertion force and screw tightening torque, comprising the following steps:

[0060] Step 1: Based on the structural design results of cylinder insert 1 and cylinder insert hole 2, determine the total interference fit between cylinder insert 1 and cylinder insert hole 2; wherein, the total interference fit δ between cylinder insert 1 and cylinder insert hole 2 is:

[0061] δ=δ e +3.2(R ao +R ai )

[0062] Wherein, δ is the total interference fit between the cylinder insert (1) and the cylinder insert hole (2); δ e The calculated value of the total interference fit between the cylinder insert (1) and the cylinder insert hole (2); R ao R is the surface roughness of the mating surface of the cylinder insert (1); ai The roughness of the mating surface of the cylinder insertion hole (2) is denoted as .

[0063] In this invention, the total interference fit between the cylinder insert 1 and the cylinder insert hole 2 includes a maximum total interference fit and a minimum total interference fit; wherein, the calculation process for the maximum total interference fit is as follows:

[0064] The maximum value of the total interference fit is obtained based on the difference between the lower deviation of the inner diameter of the cylinder insertion hole 2 and the upper deviation of the outer diameter of the cylinder insertion tube 1.

[0065] The maximum value of the total interference fit is calculated based on the maximum value of the total interference fit, combined with the surface roughness of the cylinder insert section 1 and the surface roughness of the cylinder insert hole 2.

[0066] The calculation process for the minimum total interference fit is as follows:

[0067] The minimum value of the total interference fit is obtained based on the difference between the upper deviation of the inner diameter of the cylinder insertion hole 2 and the lower deviation of the outer diameter of the cylinder insertion tube 1. Based on the minimum value of the total interference fit, combined with the roughness of the mating surface of the cylinder insertion tube 1 and the roughness of the mating surface of the cylinder insertion hole 2, the minimum value of the total interference fit is calculated. The minimum value of the total interference fit is greater than 10 mm to ensure that there is no working fluid leakage at the interference fit connection of the cylinder insertion tube.

[0068] Step 2: Based on the total interference fit between the cylinder insertion tube 1 and the cylinder insertion tube hole 2, calculate the pressing force required for the pressing process; wherein, the pressing force F required for the pressing process is:

[0069] F=Pπd i外 Lμ

[0070]

[0071]

[0072]

[0073] Where, d i内 d is the inner diameter of the cylinder insert; i外 d is the outer diameter of the cylinder insert; o内 d is the diameter of the cylinder insertion hole; o外 The height of the cylinder is μ; the coefficient of friction between the cylinder insert and the cylinder insert hole is E. i E represents the elastic modulus of the cylinder insertion tube. o V is the elastic modulus of the cylinder insertion hole. o V is the Poisson's ratio for cylinder insertion. i C is the Poisson's ratio of the cylinder insertion hole. o C is the stiffness coefficient of the cylinder insertion tube; i This is the stiffness coefficient of the cylinder insertion hole.

[0074] Step 3: Based on the cylinder's structural design, calculate the maximum value of the compressed gas force in the pump body assembly; wherein, the maximum value of the compressed gas force in the pump body assembly is:

[0075] F p =(P d -P s )×H×L

[0076] Among them, F p P is the maximum value of the compressed gas force in the pump assembly; d P is the discharge pressure under the maximum differential pressure condition that the compressor may encounter during operation. sH is the suction pressure under the maximum differential pressure condition that the compressor may encounter during operation; L is the cylinder height; and L is the projected length of the compressed gas acting within the pump body.

[0077] Step 4: Determine the frictional force required between the cylinder head 4 and the cylinder end face based on the pressing force required for the pressing process and the maximum value of the compressed gas force in the pump body assembly.

[0078] The frictional force required between the cylinder head 4 and the cylinder end face satisfies:

[0079] f′ min >F p

[0080] f′ min >F

[0081] Where, f′ min >F p F is the minimum frictional force required between the cylinder head and the cylinder end face. p F represents the maximum force of the compressed gas in the pump assembly; F is the force required for the insertion process.

[0082] That is, the minimum frictional force required between the cylinder head 4 and the cylinder end face is greater than the maximum force required for the insertion process, and the minimum frictional force required between the cylinder head 4 and the cylinder end face is greater than the maximum force of the compressor gas in the pump assembly.

[0083] Step 5: Determine the total preload of all screws on the cylinder head 4 based on the required friction between the cylinder head 4 and the cylinder end face; wherein, the total preload of all screws on the cylinder head 4 is f′. min >F p for:

[0084]

[0085] Where f′ is the frictional force required between the cylinder head and the cylinder end face; F p The maximum value of the compressed gas force in the pump body assembly; μ f This is the coefficient of friction between the cylinder head and the cylinder mating surface.

[0086] Step 6: Based on the total preload of all screws on the cylinder head 4, obtain the preload of a single screw on the cylinder head 4, and then obtain the tightening torque of a single screw.

[0087] The preload force of a single screw on the cylinder head 4 is:

[0088]

[0089] Among them, F oF is the preload force of a single bolt on the cylinder head. n is the total number of individual screws on the cylinder head; n is the total number of individual screws on the cylinder head.

[0090] The tightening torque of the single screw is:

[0091] T = KF o d≥T1+T2

[0092] Where K is the screw tightening factor; d is the nominal diameter of the screw; T1 is the thread resistance torque of the screw thread pair; and T2 is the end face friction torque between the screw end face and the support surface.

[0093] The design principles are as follows:

[0094] In the pump body assembly of a rotary compressor, the tightening torque of the screws on the cylinder is mainly to generate a preset preload between the cylinder head and the cylinder end face, so as to meet the requirements of rigidity, tightness and anti-loosening capability of the connection of various components in the pump body assembly. When the compressor is running, the frictional force generated by the preload between the cylinder head and the cylinder end face must be sufficient to overcome the compressed gas force in the pump body assembly, thereby preventing lateral movement of the components in the pump body assembly. Therefore, in the design process of screw tightening torque, it is necessary to ensure that the frictional force generated between the cylinder head and the cylinder end face by the minimum preload is greater than the maximum value of the compressed gas force in the pump body assembly; that is, to minimize the screw tightening torque while preventing lateral movement of the components in the pump body assembly.

[0095] Based on the specific structure of the compressor pump body assembly, through force analysis and theoretical calculation, the total interference fit between the cylinder insert and the cylinder insert hole is determined, and the pressing force required for the pressing process is obtained. By determining the maximum value of the compressed gas force in the pump body assembly, and under the premise that the pressing force during the pressing process is less than the frictional force between the cylinder head and the cylinder end face to prevent lateral displacement of the parts in the pump body assembly, the calculation method of the frictional force required between the cylinder head and the cylinder end face is obtained. Then, the tightening torque of the screw is determined, and finally the coupling design result of the pressing force and the screw tightening torque is realized.

[0096] The specific quantitative calculation process is as follows:

[0097] (1) Theoretical calculation process of the indentation force required for the indentation process:

[0098] For rotary compressors, gas is drawn in from the liquid reservoir during operation and enters the cylinder through the cylinder insert. During this process, the cylinder insert connects the outlet of the liquid reservoir to the inlet of the cylinder. In the existing assembly process, an interference fit is used to press the cylinder insert into the cylinder insert hole of the cylinder to ensure the airflow channel is sealed.

[0099] During the process of pressing the cylinder insert into the cylinder bore using an interference fit connection, the cylinder insert is subjected to an insertion force F applied by the insert clamp and a frictional force f1 from the wall of the cylinder insert bore. After the cylinder insert is pressed into the cylinder bore, due to the interference fit between the cylinder insert and the cylinder bore, a mutual squeezing effect will occur between them, that is, there is an interactive pressure on the mating surfaces of the cylinder insert and the cylinder bore. As the pressing depth of the cylinder insert increases, the range of the interactive pressure increases, and the frictional force f1 from the wall of the cylinder insert bore also increases accordingly.

[0100] Therefore, during the process of pressing the cylinder tube in, the following conditions must be met:

[0101] F-f1=ma>0

[0102] Where m is the mass of the cylinder inserting the tube; a is the acceleration during the cylinder inserting the tube.

[0103] Therefore, the calculation process for the indentation force F required during the indentation process is as follows:

[0104] F=Pπd i外 Lμ

[0105]

[0106] δ=δ e +3.2(R ao +R ai )

[0107]

[0108]

[0109] Where, d i内 d is the inner diameter of the cylinder insert; i外 d is the outer diameter of the cylinder insert; o内 d is the diameter of the cylinder insertion hole; o外 The height of the cylinder is μ; the coefficient of friction between the cylinder insert and the cylinder insert hole is E. i E represents the elastic modulus of the cylinder insertion tube. o V is the elastic modulus of the cylinder insertion hole. o V is the Poisson's ratio for cylinder insertion. i C is the Poisson's ratio of the cylinder insertion hole. o C is the stiffness coefficient of the cylinder insertion tube; i δ is the stiffness coefficient of the cylinder insertion hole; δ is the total interference fit between the cylinder insertion tube and the cylinder insertion hole; δ e The calculated value of the total interference fit between the cylinder insert and the cylinder insert hole; R aoR is the surface roughness of the mating surface of the cylinder insert; ai The roughness of the mating surface of the cylinder insertion hole.

[0110] (2) Theoretical calculation process of the tightening torque of the pump body cylinder screws:

[0111] In a rotary compressor, a pump body assembly is formed by fastening screws to the cylinder head and the cylinder head by creating threaded holes in the cylinder and corresponding connecting holes in the cylinder head, with the screws being tightened under their preload torque.

[0112] By adjusting the tightening torque of the screws, the connection performance of the components in the pump body assembly can be enhanced, and slippage of the screw connections can be prevented under lateral loads. When the tightening torque of the screws is too small, that is, when the frictional force indirectly generated between the cylinder head and the cylinder end face is insufficient to resist the lateral load, the screw connection structure will slip, which will cause a change in the minimum radial clearance between the cylinder and the rolling piston in the pump body assembly or a change in the centering angle of the minimum radial clearance between the cylinder and the rolling piston, ultimately affecting the product performance of the compressor. During the tightening process, the tightening torque T applied by the torque wrench must overcome the thread resistance T1 of the threaded pair and the end-face friction torque T2 between the screw end face and the support surface; that is, the tightening torque of the screws satisfies:

[0113] T = KF o d≥T1+T2

[0114] Where K is the tightening factor of the screw, K = 0.18-0.21; d is the nominal diameter of the screw; F o F is the preload force of a single bolt on the cylinder head. n This is the total preload of all bolts on the cylinder head.

[0115] The preload force of a single screw on the cylinder head is:

[0116]

[0117]

[0118] Where n is the total number of individual screws on the cylinder head; F n μ is the total number of individual screws on the cylinder head. f μ is the coefficient of friction between the cylinder head and the cylinder mating surface. f =0.10-0.15; T1 is the thread resistance torque of the screw thread pair; T2 is the end face friction torque between the screw end face and the support surface.

[0119] The frictional force between the top cover and the cylinder end face satisfies: f′=F n ×μ f >F p;

[0120] The force required for cannulation during insertion satisfies: F < f′ = F n ×μ f .

[0121] During the design of the pump body assembly, the stress state of the screws is calculated according to the stress state, thereby selecting the screw diameter, grade, quantity, and preload. Considering reliability, the tightening torque is then determined, and the friction force between the top cover and the cylinder wall is also obtained. Subsequently, the tightening torque of the screws is tested for reliability as follows: 1) During operation, the maximum resultant force of the compressed gas generated in the working chamber of the pump body is less than the friction force between the top cover and the cylinder end face; 2) During assembly, when the cylinder insert is pressed in, the applied lateral load will not exceed the friction force between the top cover and the cylinder wall, preventing changes in the radial clearance value between the cylinder and the rotor or changes in the centering angle of the radial clearance value between the cylinder and the rotor.

[0122] In this invention, when the pressing force is insufficient to press the cylinder tube into the cylinder and the applied lateral load exceeds the friction between the cylinder head and the cylinder end face, the following two adjustments are made: First, the maximum value of the total interference fit between the cylinder tube and the cylinder tube hole is reduced to reduce the pressing force required for the pressing process; second, the end face preload is adjusted by adjusting the cylinder screw tightening torque to adjust the friction. The adjustment of the cylinder screw tightening torque is achieved by changing the number of screws, their diameter, and the tightening torque of a single screw.

[0123] In this invention, by obtaining the interference fit between the cylinder insert tube and the cylinder insert tube hole, it is ensured that when the cylinder presses into the insert tube, there is no working fluid leakage at the interference fit connection of the cylinder insert tube when the interference fit is at its minimum; and when the interference fit is at its maximum, the pressing force of the insert tube must be less than the frictional force generated between the upper and lower covers and the cylinder end face to prevent lateral displacement. The design method of this invention organically combines the pressing force of the insert tube with the tightening torque of the screw, and performs a coupled design, which can comprehensively consider the limitation range of both, thereby meeting the design requirements.

[0124] Experimental results:

[0125] In this invention, based on the coupling design method of the insertion force and screw tightening torque, and combined with the compressor pump body structure, calculations are performed on a compressor product with a displacement Vs = 4.3cc, using R32 working fluid. The calculation results of the insertion force of the cylinder tube, the frictional force between the cylinder head and the cylinder end face, and the maximum value of the compressed gas force in the pump body assembly are shown in Tables 1-3 below:

[0126] Table 1 Calculation results of cylinder insertion force

[0127]

[0128] Table 2 Calculation results of frictional force between cylinder head and cylinder end face.

[0129] Screw thread nominal diameter (mm) M4 Number of screws 5 Tightening torque N·m 5±0.3 K 0.18～0.21 Preload N 5595～7361 coefficient of friction 0.10～0.15 Friction N 2798～5521

[0130] Table 3 Calculation results of the maximum value of compressed gas force in the pump body assembly.

[0131]

[0132] As can be seen from Tables 1-3 above, under the condition that the interference fit between the cylinder head and the cylinder head hole is 5-27 μm, the required insertion force is 679-2092 N; the friction force between the cylinder head and the cylinder end face is 2798-5521 N; and the maximum value of the compressed gas force in the pump body assembly is 1703.8 N. Therefore, the above calculation results all meet the requirements that the minimum friction force required between the cylinder head and the cylinder end face is greater than the maximum insertion force required for the insertion process, and the minimum friction force required between the cylinder head and the cylinder end face is greater than the maximum value of the compressed gas force in the pump body assembly.

[0133] This invention also provides a coupling design system for insertion force and screw tightening torque, including an overall assembly interference module, an insertion force module, a gas force module, a friction force module, an overall preload force module, and a tightening torque module; wherein, the overall assembly interference module is used to determine the overall fit interference between cylinder insertion tube 1 and cylinder insertion hole 2 based on the structural design results of cylinder insertion tube 1 and cylinder insertion hole 2; the insertion force module is used to calculate the insertion force required for the insertion process based on the overall fit interference between cylinder insertion tube 1 and cylinder insertion hole 2; the gas force module is used to calculate the maximum value of the compressed gas force in the pump assembly based on the structural design results of the cylinder; the friction force module is used to calculate the maximum value of the compressed gas force in the pump assembly based on the insertion process... The required force for inserting the tube and the maximum value of the compressed gas force in the pump body assembly are used to determine the required friction force between the cylinder head 4 and the cylinder end face. The minimum required friction force between the cylinder head 4 and the cylinder end face is greater than the maximum required force for inserting the tube during the insertion process, and the minimum required friction force between the cylinder head 4 and the cylinder end face is greater than the maximum value of the compressed gas force in the pump body assembly. A total preload module is used to determine the total preload force of all screws on the cylinder head 4 based on the required friction force between the cylinder head 4 and the cylinder end face. A tightening torque module is used to obtain the preload force of a single screw on the cylinder head 4 based on the total preload force of all screws on the cylinder head 4, and thus obtain the tightening torque of the single screw.

[0134] The present invention also provides a coupling design device for inserting cannula force and screw tightening torque, comprising: a memory for storing a computer program; and a processor for executing the computer program to implement the steps of the coupling design method for inserting cannula force and screw tightening torque.

[0135] When the processor executes the computer program, it implements the steps of the above-mentioned coupling design method for the insertion force and screw tightening torque, for example: determining the total interference fit between the cylinder insertion tube 1 and the cylinder insertion hole 2 based on the structural design results of the cylinder insertion tube 1 and the cylinder insertion hole 2; calculating the insertion force required for the insertion process based on the total interference fit between the cylinder insertion tube 1 and the cylinder insertion hole 2; calculating the maximum value of the compressed gas force in the pump body assembly based on the structural design results of the cylinder; and calculating the maximum value of the compressed gas force in the pump body assembly based on the insertion force required for the insertion process and the maximum value of the compressed gas force in the pump body assembly. The required friction force between cylinder head 4 and cylinder end face is determined; wherein, the minimum required friction force between cylinder head 4 and cylinder end face is greater than the maximum required force for the insertion of the tube during the insertion process, and the minimum required friction force between cylinder head 4 and cylinder end face is greater than the maximum required force of the compressor gas in the pump body assembly; based on the required friction force between cylinder head 4 and cylinder end face, the total preload of all screws on cylinder head 4 is determined; based on the total preload of all screws on cylinder head 4, the preload of a single screw on cylinder head 4 is obtained, and thus the tightening torque of a single screw is obtained.

[0136] Alternatively, when the processor executes the computer program, it implements the functions of each module in the above system, such as: a total assembly interference module, used to determine the total interference fit between cylinder insert 1 and cylinder insert hole 2 based on the structural design results of cylinder insert 1 and cylinder insert hole 2; a pressing force module, used to calculate the pressing force required for the pressing process based on the total interference fit between cylinder insert 1 and cylinder insert hole 2; a gas force module, used to calculate the maximum value of the compressed gas force in the pump body assembly based on the structural design results of the cylinder; and a friction force module, used to calculate the pressing force required for the pressing process and the compressed gas force in the pump body assembly. The maximum value of the force determines the required frictional force between the cylinder head 4 and the cylinder end face; wherein, the minimum value of the required frictional force between the cylinder head 4 and the cylinder end face is greater than the maximum value of the pressing force required for the pressing process, and the minimum value of the required frictional force between the cylinder head 4 and the cylinder end face is greater than the maximum value of the compressor gas force in the pump body assembly; the total preload module is used to determine the total preload of all screws on the cylinder head 4 based on the required frictional force between the cylinder head 4 and the cylinder end face; the tightening torque module is used to obtain the preload of a single screw on the cylinder head 4 based on the total preload of all screws on the cylinder head 4, and then obtain the tightening torque of a single screw.

[0137] For example, the computer program can be divided into one or more modules / units, which are stored in the memory and executed by the processor to complete the present invention. The one or more modules / units can be a series of computer program instruction segments capable of performing preset functions, wherein the instruction segments describe the execution process of the computer program in the coupled design device of the insertion force and screw tightening torque. For example, the computer program can be divided into: an overall assembly interference module, an insertion force module, a gas force module, a friction force module, an overall preload force module, and a tightening torque module.

[0138] The specific functions of each module are as follows: The overall assembly interference module is used to determine the total interference fit between cylinder tube 1 and cylinder tube hole 2 based on the structural design results of cylinder tube 1 and cylinder tube hole 2; the tube insertion force module is used to calculate the tube insertion force required for the tube insertion process based on the total interference fit between cylinder tube 1 and cylinder tube hole 2; the gas force module is used to calculate the maximum value of the compressed gas force in the pump body assembly based on the cylinder's structural design results; and the friction force module is used to determine the cylinder head based on the tube insertion force required for the tube insertion process and the maximum value of the compressed gas force in the pump body assembly. 4. The required frictional force between the cylinder head 4 and the cylinder end face; wherein, the minimum value of the required frictional force between the cylinder head 4 and the cylinder end face is greater than the maximum value of the pressing force required for the pressing process, and the minimum value of the required frictional force between the cylinder head 4 and the cylinder end face is greater than the maximum value of the compressor gas force in the pump body assembly; the total preload module is used to determine the total preload of all screws on the cylinder head 4 based on the required frictional force between the cylinder head 4 and the cylinder end face; the tightening torque module is used to obtain the preload of a single screw on the cylinder head 4 based on the total preload of all screws on the cylinder head 4, and then obtain the tightening torque of a single screw.

[0139] The coupling design device for the insertion force and screw tightening torque can be a computing device such as a desktop computer, laptop, handheld computer, or cloud server. This coupling design device may include, but is not limited to, processors and memory. Those skilled in the art will understand that the above are examples of coupling design devices for insertion force and screw tightening torque and do not constitute a limitation on such devices. The device may include more components than described above, or combine certain components, or use different components. For example, the coupling design device for insertion force and screw tightening torque may also include input / output devices, network access devices, buses, etc.

[0140] The processor referred to can be a Central Processing Unit (CPU), or other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), field-programmable gate arrays (FPGAs), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. The general-purpose processor can be a microprocessor, or any conventional processor. The processor is the control center of the coupling design device for the insertion force and screw tightening torque, connecting all parts of the coupling design device using various interfaces and lines.

[0141] The memory can be used to store the computer program and / or module. The processor realizes various functions of the coupling design device for the insertion force and screw tightening torque by running or executing the computer program and / or module stored in the memory and calling the data stored in the memory.

[0142] The memory may primarily include a program storage area and a data storage area. The program storage area may store the operating system and at least one application program required for a given function (such as sound playback or image playback). The data storage area may store data created based on the use of the phone (such as audio data or a phonebook). Furthermore, the memory may include high-speed random access memory (RAM) and non-volatile memory, such as hard disks, RAM, plug-in hard disks, SmartMediaCards (SMC), Secure Digital (SD) cards, flash cards, at least one disk storage device, flash memory device, or other volatile solid-state storage devices.

[0143] In this invention, the minimum total interference fit between the cylinder insert and the cylinder insert hole satisfies the sealing of the airflow channel, and the maximum total interference fit ensures that the lateral load generated when the insert is pressed in is insufficient to cause lateral displacement between the parts in the pump body assembly; the minimum frictional force between the cylinder head and the cylinder end face generated by the screw tightening torque must be sufficient to resist the lateral load and the maximum compressed gas force generated when the insert is pressed in, so as to prevent lateral displacement and ensure the performance of the product.

[0144] The coupling design method described in this invention is applicable to compressors used in different refrigerant applications, under different operating conditions, with different displacements, and in different application fields; wherein, compressors used in different application fields include air conditioning, heat pump heating, or refrigeration.

[0145] The above embodiments are merely one of the implementation methods for achieving the technical solution of the present invention. The scope of protection claimed by the present invention is not limited to this embodiment, but also includes any variations, substitutions and other implementation methods that can be easily conceived by those skilled in the art within the scope of the technology disclosed in the present invention.

Claims

1. A coupling design method for insertion force and screw tightening torque, characterized in that, include: Based on the structural design results of the cylinder insert (1) and the cylinder insert hole (2), the total interference fit between the cylinder insert (1) and the cylinder insert hole (2) is determined. Based on the total interference fit between the cylinder insertion tube (1) and the cylinder insertion tube hole (2), the pressing force required for the pressing tube process is calculated. Based on the structural design results of the cylinder, calculate the maximum value of the compressed gas force in the pump body assembly; Based on the insertion force required for the insertion process and the maximum value of the compressed gas force in the pump body assembly, the frictional force required between the cylinder head (4) and the cylinder end face is determined; wherein, the minimum value of the frictional force required between the cylinder head (4) and the cylinder end face is greater than the maximum value of the insertion force required for the insertion process, and the minimum value of the frictional force required between the cylinder head (4) and the cylinder end face is greater than the maximum value of the compressed gas force in the pump body assembly; The total preload of all screws on the cylinder head (4) is determined based on the required friction between the cylinder head (4) and the cylinder end face; Based on the total preload of all screws on the cylinder head (4), the preload of a single screw on the cylinder head (4) is obtained, and then the tightening torque of a single screw is obtained.

2. The coupling design method for the insertion force and screw tightening torque according to claim 1, characterized in that, The total interference fit between the cylinder insert (1) and the cylinder insert hole (2) for: in, The total interference fit between the cylinder insert (1) and the cylinder insert hole (2) is the total amount of interference fit. The total interference fit between the cylinder insert (1) and the cylinder insert hole (2) is calculated. The surface roughness of the mating surface of the cylinder insert (1); The roughness of the mating surface of the cylinder insertion hole (2) is denoted as .

3. The coupling design method for the insertion force and screw tightening torque according to claim 2, characterized in that, The total interference fit between the cylinder insert (1) and the cylinder insert hole (2) includes the maximum total interference fit and the minimum total interference fit. The calculation process for the maximum total interference fit is as follows: The maximum value of the total interference fit is obtained based on the difference between the lower deviation of the inner diameter of the cylinder insertion hole (2) and the upper deviation of the outer diameter of the cylinder insertion tube (1). The maximum value of the total interference fit is calculated based on the maximum value of the total interference fit, combined with the surface roughness of the cylinder insert (1) and the surface roughness of the cylinder insert hole (2). The calculation process for the minimum total interference fit is as follows: The minimum value of the total interference fit is obtained based on the difference between the upper deviation of the inner diameter of the cylinder insertion hole (2) and the lower deviation of the outer diameter of the cylinder insertion tube (1). The minimum value of the total interference fit is calculated based on the minimum value of the total interference fit, combined with the surface roughness of the cylinder insert (1) and the surface roughness of the cylinder insert hole (2).

4. The coupling design method for the insertion force and screw tightening torque according to claim 3, characterized in that, The minimum total interference fit is greater than 10 μm.

5. The coupling design method for the insertion force and screw tightening torque according to claim 1, characterized in that, The force required for the cannulation process F for: in, This refers to the inner diameter of the cylinder insertion tube; The outer diameter of the cylinder insertion tube; This refers to the diameter of the cylinder insertion hole; The height of the cylinder; The coefficient of friction is the mating surface between the cylinder insert and the cylinder insert hole. The elastic modulus of the cylinder insertion tube; The elastic modulus of the cylinder insertion hole; Poisson's ratio for cylinder insertion; Poisson's ratio for the cylinder insertion port; This is the stiffness coefficient of the cylinder insertion tube; The stiffness coefficient of the cylinder insertion hole; The projected length of the compressed gas acting within the pump body; The total interference fit between the cylinder insert (1) and the cylinder insert hole (2) is the total interference fit.

6. The coupling design method for the insertion force and screw tightening torque according to claim 1, characterized in that, The maximum value of the compressed gas force in the pump assembly is: in, This represents the maximum value of the compressed gas force in the pump assembly; This refers to the discharge pressure under the maximum differential pressure condition that the compressor may encounter during operation. This is the suction pressure under the maximum differential pressure condition that the compressor may encounter during operation; This refers to the cylinder height; This is the projected length of the compressed gas within the pump body.

7. The coupling design method for the insertion force and screw tightening torque according to claim 1, characterized in that, Tightening torque of a single screw T for: in, This is the tightening factor of the screw; This is the nominal diameter of the screw; This represents the total number of individual bolts on the cylinder head. Preload force for a single bolt on the cylinder head; This represents the total number of individual bolts on the cylinder head. This represents the maximum value of the compressed gas force within the pump assembly; The coefficient of friction between the cylinder head and the cylinder mating surface; T 1 represents the thread resistance torque of the screw thread pair; T 2 represents the end-face friction torque between the screw end face and the support surface; This is the frictional force required between the cylinder head and the cylinder end face; This is the minimum frictional force required between the cylinder head and the cylinder end face; F This refers to the force required for the insertion of the cannula during the insertion process.

8. A coupling design system for insertion force and screw tightening torque, characterized in that, include: The overall assembly interference module is used to determine the total interference fit between the cylinder tube (1) and the cylinder tube hole (2) based on the structural design results of the cylinder tube (1) and the cylinder tube hole (2). The insertion force module is used to calculate the insertion force required for the insertion process based on the total interference fit between the cylinder insertion tube (1) and the cylinder insertion tube hole (2). The gas force module is used to calculate the maximum value of the compressed gas force in the pump body assembly based on the structural design results of the cylinder. The friction module is used to determine the friction force required between the cylinder head (4) and the cylinder end face based on the pressing force required for the pressing process and the maximum value of the compressed gas force in the pump body assembly; wherein, the minimum value of the friction force required between the cylinder head (4) and the cylinder end face is greater than the maximum value of the pressing force required for the pressing process, and the minimum value of the friction force required between the cylinder head (4) and the cylinder end face is greater than the maximum value of the compressed gas force in the pump body assembly; The total preload module is used to determine the total preload of all screws on the cylinder head (4) based on the required friction between the cylinder head (4) and the cylinder end face; The tightening torque module is used to obtain the preload of a single screw on the cylinder head (4) based on the total preload of all screws on the cylinder head (4), and then obtain the tightening torque of the single screw.

9. A device for coupling the insertion force and the screw tightening torque, characterized in that, include: Memory, used to store computer programs; A processor, configured to implement the steps of the coupling design method for inserting tube force and screw tightening torque as described in any one of claims 1-7 when executing the computer program.

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