A Design Method, System, Device and Medium for Spiral Oil Groove

Abstract

The present invention discloses a spiral oil groove design method, system, device and medium, including: performing a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston; determining the compressed area of the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; obtaining the zero-compression area of the inner wall surface of the bearing according to the compressed area of the inner wall surface of the bearing during the rotation of the crankshaft, that is, obtaining the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing; by performing a force analysis on the rolling piston, the present invention takes the zero-compression area of the inner wall surface of the bearing as the layout area of the spiral oil groove to be designed, avoids the wear of the spiral oil groove during the rotation of the crankshaft, ensures the reliability of the lubrication effect between the crankshaft-bearing cover moving pair, effectively reduces the power consumption of the crankshaft-bearing cover moving pair, and improves the reliability of the compressor pump body.

Description

Technical Field

[0001] The present invention belongs to the technical field of rotary compressor design, and particularly relates to a spiral oil groove design method, system, device and medium. Background Art

[0002] With the development of technology, the requirements for the reliability and energy efficiency of rotary compressors are getting higher and higher; for this reason, it is necessary to optimize the design of the pump body lubrication structure to improve lubrication reliability, reduce friction and power consumption; among them, the design of the spiral oil groove on the inner hole wall of the bearing of the upper bearing cover or the lower bearing cover of the compressor pump body is one of the main design bottlenecks affecting lubrication reliability, friction and power consumption.

[0003] Currently, for the spiral oil groove on the inner hole wall of the bearing of the upper bearing cover or the lower bearing cover, most refer to the design results of the existing spiral oil groove; when the structural parameters of the upper bearing cover or the lower bearing cover change, due to the lack of corresponding theoretical basis for reference design, during the operation of the compressor pump body, the wear of the spiral oil groove is relatively large, increasing the friction power consumption of the crankshaft-bearing cover moving pair, and seriously affecting the reliability of the compressor. Summary of the Invention

[0004] Aiming at the technical problems existing in the prior art, the present invention provides a spiral oil groove design method and system for the inner hole wall of a bearing to solve the technical problems that in the design process of the spiral oil groove in the prior art, due to the lack of corresponding theoretical design basis, during the operation of the compressor pump body, the wear of the spiral oil groove is relatively large, increasing the friction power consumption of the crankshaft-bearing cover moving pair, and seriously affecting the reliability of the compressor.

[0005] To achieve the above object, the technical solution adopted by the present invention is as follows:

[0006] The present invention provides a spiral oil groove design method, which is used to determine the layout area of the spiral oil groove on the inner hole wall of the bearing of the upper bearing cover or the lower bearing cover of the compressor pump body;

[0007] Among them, the design method includes:

[0008] According to the structural characteristics of the compressor pump body, perform a force analysis on the rolling piston to obtain the resultant external force of all the resistances acting on the rolling piston;

[0009] According to the resultant external force of all the resistances acting on the rolling piston, determine the pressure-bearing area of the inner hole wall of the bearing during the rotation of the crankshaft;

[0010] According to the pressure-bearing area of the inner hole wall of the bearing during the rotation of the crankshaft, obtain the zero-pressure-bearing area of the inner hole wall of the bearing, that is, obtain the layout area of the spiral oil groove to be designed on the inner hole wall of the bearing.

[0011] Further, all the resistances acting on the rolling piston include: the gas force F acting on the rolling piston g , the radial contact force F between the rolling piston and the sliding vane n , the tangential contact force F between the rolling piston and the sliding vane t and the rotational inertia force F of the rolling piston 1p .

[0012] Further, the process of determining the pressure - bearing area on the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston is as follows:

[0013] Determine the direction of the resultant external force acting on the rolling piston according to the resultant external force of all the resistances acting on the rolling piston;

[0014] Determine the pressure - bearing range on the inner wall surface of the bearing during the rotation of the crankshaft according to the direction of the resultant external force acting on the rolling piston, that is, obtain the pressure - bearing area on the inner wall surface of the bearing during the rotation of the crankshaft.

[0015] Further, the zero - pressure - bearing area on the inner wall surface of the bearing is: on the inner wall surface of the bearing, the wall surface area outside the pressure - bearing area on the inner wall surface of the bearing during the rotation of the crankshaft.

[0016] Further, after obtaining the zero - pressure - bearing area on the inner wall surface of the bearing according to the pressure - bearing area on the inner wall surface of the bearing during the rotation of the crankshaft, that is, obtaining the layout area of the to - be - designed spiral oil groove on the inner wall surface of the bearing, an initial - point correction step is also included;

[0017] Among them, the initial - point correction step is as follows:

[0018] Calculate the start - stop angle Δγ of the to - be - designed spiral oil groove according to the height h of the inner bore of the bearing and the pitch p of the oil groove of the to - be - designed spiral oil groove;

[0019] Compare the start - stop angle Δγ of the to - be - designed spiral oil groove with the layout area of the to - be - designed spiral oil groove on the inner wall surface of the bearing. If the start - stop angle Δγ of the to - be - designed spiral oil groove is greater than the angle of the layout area of the to - be - designed spiral oil groove on the inner wall surface of the bearing, move the starting point of the to - be - designed spiral oil groove a preset distance towards the suction side of the compressor pump body to ensure that the end point of the to - be - designed spiral oil groove is within the layout area of the to - be - designed spiral oil groove on the inner wall surface of the bearing.

[0020] Further, the process of determining the start - stop angle Δγ of the to - be - designed spiral oil groove is as follows:

[0021] Calculate the start - stop angle Δγ of the to - be - designed spiral oil groove according to the height h of the inner bore of the bearing and the pitch p of the oil groove of the to - be - designed spiral oil groove.

[0022] Furthermore, the start and end angles Δγ of the spiral oil groove to be designed are as follows:

[0023]

[0024] The present invention also provides a spiral oil groove design system, which is used to determine the layout area of the spiral oil groove on the bearing inner hole wall of the upper bearing cover or the lower bearing cover in the compressor pump body;

[0025] Among them, the design system includes:

[0026] A force analysis module, which is used to perform a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston;

[0027] A compression area determination module, which is used to determine the compression area of the bearing inner hole wall surface during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston;

[0028] A layout area determination module, which is used to obtain the zero-compression area of the bearing inner hole wall surface according to the compression area of the bearing inner hole wall surface during the rotation of the crankshaft, that is, to obtain the layout area of the spiral oil groove to be designed on the bearing inner hole wall surface.

[0029] The present invention also provides a spiral oil groove design device, including:

[0030] A memory, which is used to store computer programs;

[0031] A processor, which is used to implement the steps of the spiral oil groove design method when executing the computer program.

[0032] The present invention also provides a computer-readable storage medium, which stores a computer program. The computer program is characterized in that when it is executed by a processor, it implements the steps of the spiral oil groove design method.

[0033] Compared with the prior art, the beneficial effects of the present invention are:

[0034] The present invention provides a spiral oil groove design method and system. By performing a force analysis on the rolling piston and determining the zero-compression area of the bearing inner hole wall surface during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston, and using the zero-compression area of the bearing inner hole wall surface as the layout area of the spiral oil groove to be designed, the wear of the spiral oil groove during the rotation of the crankshaft is avoided, the reliability of the lubrication effect between the crankshaft-bearing cover moving pair is ensured, the power consumption of the crankshaft-bearing cover moving pair is effectively reduced, and the reliability of the compressor pump body is improved.

[0035] Further, compare the start and end angles Δγ of the spiral oil groove to be designed with the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing bore, and adjust the starting point of the spiral oil groove to be designed according to the comparison result; by locating the starting point of the spiral oil groove to be designed in the area with relatively low compressive pressure on the inner wall surface of the bearing bore, it is further ensured that the end point of the spiral oil groove to be designed does not fall in the area with relatively high compressive pressure on the inner wall surface of the bearing bore, thereby ensuring the lubrication effect at the contact surface of the crankshaft-bearing cap kinematic pair. Brief Description of the Drawings

[0036] Figure 1 is a longitudinal sectional view of the upper bearing cap in the embodiment;

[0037] Figure 2 is a schematic plan view of the upper bearing cap in the embodiment;

[0038] Figure 3 is a force analysis diagram of the rolling piston in the embodiment;

[0039] Figure 4 is a diagram showing the variation of the direction of the resultant external force acting on the rolling piston with the crankshaft rotation angle in the embodiment;

[0040] Figure 5 is a diagram showing the variation of the magnitude of the resultant external force acting on the rolling piston with the crankshaft rotation angle in the embodiment.

[0041] Wherein, 1 is the upper bearing cap, 2 is the rolling piston, 3 is the spiral oil groove to be designed, and 4 is the sliding vane. Detailed Embodiment

[0042] In order to make the technical problems, technical solutions and beneficial effects solved by the present invention clearer and more understandable, the following specific embodiments are used to further elaborate on the present invention in detail. It should be understood that the specific embodiments described herein are only for explaining the present invention and are not used to limit the present invention.

[0043] The present invention provides a method for designing a spiral oil groove, which is used to determine the layout area of the spiral oil groove on the inner wall surface of the bearing bore of the upper bearing cap or the lower bearing cap of the compressor pump body; wherein, the design method includes the following steps:

[0044] According to the structural characteristics of the compressor pump body, perform a force analysis on the rolling piston to obtain the resultant external force of all the resistances acting on the rolling piston; wherein, all the resistances acting on the rolling piston include: the gas force F acting on the rolling piston g , the radial contact force F between the rolling piston and the sliding vane n , the tangential contact force F between the rolling piston and the sliding vane t and the rotational inertia force F of the rolling piston 1p .

[0045] Determine the pressure-bearing area on the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; specifically, determine the direction of the resultant external force acting on the rolling piston according to the resultant external force of all the resistances acting on the rolling piston; and determine the pressure-bearing range on the inner wall surface of the bearing during the rotation of the crankshaft according to the direction of the resultant external force acting on the rolling piston, that is, obtain the pressure-bearing area on the inner wall surface of the bearing during the rotation of the crankshaft.

[0046] Obtain the zero-pressure-bearing area on the inner wall surface of the bearing according to the pressure-bearing area on the inner wall surface of the bearing during the rotation of the crankshaft, that is, obtain the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing; wherein, the zero-pressure-bearing area on the inner wall surface of the bearing is: on the inner wall surface of the bearing, the wall surface area outside the pressure-bearing area on the inner wall surface of the bearing during the rotation of the crankshaft.

[0047] Calculate the start-stop angle Δγ of the to-be-designed spiral oil groove according to the height h of the inner bore of the bearing and the pitch p of the oil groove of the to-be-designed spiral oil groove; wherein, the process of determining the start-stop angle Δγ of the to-be-designed spiral oil groove is as follows:

[0048] Calculate the start-stop angle Δγ of the to-be-designed spiral oil groove according to the height h of the inner bore of the bearing and the pitch p of the oil groove of the to-be-designed spiral oil groove;

[0049] wherein, the start-stop angle Δγ of the to-be-designed spiral oil groove is:

[0050]

[0051] Compare the start-stop angle Δγ of the to-be-designed spiral oil groove with the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing. If the start-stop angle Δγ of the to-be-designed spiral oil groove is greater than the angle of the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing, move the starting point of the to-be-designed spiral oil groove a preset distance towards the suction side of the compressor pump body to ensure that the termination point of the to-be-designed spiral oil groove is within the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing.

[0052] The spiral oil groove design method of the present invention quantitatively calculates the resultant external force of all the resistances acting on the rolling piston to determine the force on the rolling piston, and further determines the force-bearing area on the inner wall surface of the bearing of the upper bearing cover or the lower bearing cover; takes the zero-pressure-bearing area on the inner wall surface of the bearing as the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing, ensures that the spiral oil groove is designed at the zero-pressure-bearing area on the inner wall surface of the bearing, ensures the reliability of the lubrication of the kinematic pair and low power consumption, and effectively improves the product performance.

[0053] The present invention also provides a spiral oil groove design system for determining the layout area of the spiral oil groove on the inner wall surface of the bearing of the upper bearing cover or the lower bearing cover in the compressor pump body; wherein, the design system includes a force analysis module, a compression area determination module, a layout area determination module and a starting point correction module: The force analysis module is used to perform a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston; The compression area determination module is used to determine the compression area of the inner wall surface of the bearing hole during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; The layout area determination module is used to obtain the zero compression area of the inner wall surface of the bearing hole according to the compression area of the inner wall surface of the bearing hole during the rotation of the crankshaft, that is, to obtain the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing hole; The starting point correction module is used to calculate the start-stop angle Δγ of the spiral oil groove to be designed according to the bearing hole h and the oil groove pitch p of the spiral oil groove to be designed; Compare the start-stop angle Δγ of the spiral oil groove to be designed with the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing hole. If the start-stop angle Δγ of the spiral oil groove to be designed is greater than the angle of the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing hole, move the starting point of the spiral oil groove to be designed a preset distance towards the suction side of the compressor pump body to ensure that the end point of the spiral oil groove to be designed is located within the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing hole.

[0054] The present invention also provides a spiral oil groove design device, including: a memory for storing a computer program; a processor for implementing the steps of the spiral oil groove design method when executing the computer program.

[0055] When the processor executes the computer program, it implements the steps of the above-mentioned spiral oil groove design method. For example: performing a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston; determining the compression area of the inner wall surface of the bearing hole during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; obtaining the zero compression area of the inner wall surface of the bearing hole according to the compression area of the inner wall surface of the bearing hole during the rotation of the crankshaft, that is, obtaining the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing hole.

[0056] Alternatively, when the processor executes the computer program, it realizes the functions of the various modules in the above system. For example: a force analysis module, which is used to perform a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston; a compression area determination module, which is used to determine the compressed area of the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; a layout area determination module, which is used to obtain the zero-compression area of the inner wall surface of the bearing according to the compressed area of the inner wall surface of the bearing during the rotation of the crankshaft, that is, to obtain the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing.

[0057] Exemplarily, the computer program can be divided into one or more modules / units, and the one or more modules / units 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, and the instruction segments are used to describe the execution process of the computer program in the spiral oil groove design device. For example, the computer program can be divided into a force analysis module, a compression area determination module, and a layout area determination module. The specific functions of each module are as follows: a force analysis module, which is used to perform a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston; a compression area determination module, which is used to determine the compressed area of the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; a layout area determination module, which is used to obtain the zero-compression area of the inner wall surface of the bearing according to the compressed area of the inner wall surface of the bearing during the rotation of the crankshaft, that is, to obtain the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing.

[0058] The spiral oil groove design device can be a computing device such as a desktop computer, a notebook, a palm computer, and a cloud server. The spiral oil groove design device may include, but is not limited to, a processor and a memory. Those skilled in the art can understand that the above are examples of the spiral oil groove design device, which do not constitute a limitation on the spiral oil groove design device. It may include more components than the above, or combine some components, or different components. For example, the spiral oil groove design device may further include input / output devices, network access devices, a bus, etc.

[0059] The so-called processor may be a Central Processing Unit (CPU), or may also be 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 may be a microprocessor, or the processor may also be any conventional processor, etc. The processor is the control center of the spiral oil groove design device, and connects various parts of the entire spiral oil groove design device through various interfaces and lines.

[0060] The memory can be used to store the computer programs and / or modules. The processor realizes various functions of the spiral oil groove design device by running or executing the computer programs and / or modules stored in the memory, and by calling the data stored in the memory.

[0061] The memory may mainly include a program storage area and a data storage area. Among them, the program storage area can store an operating system, application programs required for at least one function (such as a sound playback function, an image playback function, etc.); the data storage area can store data created according to the use of the mobile phone (such as audio data, phone book, etc.). In addition, the memory may include high-speed random access memory, and may also include non-volatile memory, such as a hard disk, memory, plug-in hard disk, Smart Media Card (SMC), Secure Digital (SD) card, Flash Card, at least one magnetic disk storage device, flash memory device, or other volatile solid-state storage devices.

[0062] The present invention also provides a computer-readable storage medium. The computer-readable storage medium stores a computer program, and when the computer program is executed by a processor, the steps of the spiral oil groove design method described above are realized.

[0063] If the modules / units integrated in the spiral oil groove design system are implemented in the form of software functional units and sold or used as independent products, they can be stored in a computer-readable storage medium.

[0064] Based on such understanding, all or part of the processes in the above-mentioned spiral oil groove design method of the present invention can also be completed by instructing relevant hardware through a computer program. The computer program can be stored in a computer-readable storage medium. When the computer program is executed by a processor, the steps of the above-mentioned spiral oil groove design method can be realized. Among them, the computer program includes computer program code, and the computer program code can be in the form of source code, object code, executable file or preset intermediate form, etc.

[0065] The computer-readable storage medium may include: any entity or device capable of carrying the computer program code, recording medium, USB flash drive, mobile hard disk, magnetic disk, optical disk, computer memory, read-only memory (ROM), random access memory (RAM), electrical carrier signal, telecommunication signal, and software distribution medium, etc.

[0066] It should be noted that the content included in the computer-readable storage medium can be appropriately increased or decreased according to the requirements of legislation and patent practice within the jurisdiction. For example, in some jurisdictions, according to legislation and patent practice, the computer-readable storage medium does not include electrical carrier signals and telecommunication signals.

[0067] Embodiment

[0068] As shown in the Figure 1-2 accompanying drawings, taking the design process of the spiral oil groove on the inner wall of the bearing hole of the upper bearing cover 1 of a certain compressor pump body as an example.

[0069] This embodiment provides a design method for a spiral oil groove, which specifically includes the following steps:

[0070] Step 1: According to the structural characteristics of the compressor pump body, perform a force analysis on the rolling piston 2 to obtain the resultant external force of all the resistances acting on the rolling piston 2; among them, all the resistances acting on the rolling piston 2 include the gas force F g acting on the rolling piston 2, the radial contact force F n between the rolling piston 2 and the sliding vane 4, the tangential contact force F t between the rolling piston 2 and the sliding vane 4, and the rotational inertia force F 1p of the rolling piston 2.

[0071] Among them, the magnitude of the resultant external force of all the resistances acting on the rolling piston 2 is:

[0072]

[0073]

[0074]

[0075]

[0076] F t = μ v F n

[0077]

[0078] F 1p = m p eω 2

[0079] Among them, ∑F is the resultant external force of all the resistances acting on the rolling piston; F r is the component force of the resultant external force acting on the rolling piston along the radial direction of the rolling piston; F θ is the component force of the resultant external force acting on the rolling piston along the tangential direction of the rolling piston; F g is the gas force acting on the rolling piston; θ is the crankshaft rotation angle; α is the angle between the connecting line of the vane centers and the center line of the vane. The connecting line of the vane centers is the line connecting the center of the arc at the R end of the vane and the center of the rolling piston; F n is the radial contact force between the rolling piston and the vane; F t is the tangential contact force between the rolling piston and the vane; F 1p is the rotational inertia force of the rolling piston; r is the outer radius of the rolling piston; H is the cylinder height; P c is the compression chamber pressure in the cylinder; P b is the suction chamber pressure in the cylinder; μ v is the friction coefficient between the vane and the rolling piston; μ is the dynamic viscosity of the lubricating oil; F h is the differential pressure force borne by the part of the vane extending into the cylinder; l0 is the radial length of the vane; μ s is the friction coefficient between the vane and the vane groove; B v is the thickness of the vane; F k is the spring force of the vane; F c is the gas differential pressure force borne at both ends of the vane; F 1v is the inertia force of the vane; x is the displacement of the vane; ΔR v is the radius of the arc at the R end of the vane; m p is the eccentric mass of the crankshaft; e is the eccentricity of the crankshaft; ω is the rotational angular velocity of the crankshaft.

[0080] The direction of the resultant external force of all the resistances acting on the rolling piston 2 is:

[0081]

[0082] Among them, θ∑ Fis the direction angle of the resultant external force acting on the rolling piston.

[0083] Step 2: Determine the pressure-bearing range of the inner wall surface of the bearing during the rotation of the crankshaft according to the direction of the resultant external force acting on the rolling piston 2, that is, obtain the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft.

[0084] Step 3: Obtain the zero pressure-bearing area of the inner wall surface of the bearing according to the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft, that is, obtain the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing; wherein, the zero pressure-bearing area of the inner wall surface of the bearing is: on the inner wall surface of the bearing, the wall surface area outside the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft.

[0085] Step 4: Determine the structural parameters of the to-be-designed spiral oil groove 3 according to the structural characteristics of the compressor pump body; wherein, the structural parameters of the to-be-designed spiral oil groove include the start and end angle Δγ of the oil groove, the start angle γ1 of the oil groove, the end angle γ2 of the oil groove and the pitch p of the oil groove.

[0086] Among them, the start and end angle Δγ of the to-be-designed spiral oil groove 3 is:

[0087]

[0088] Among them, h is the height of the inner bore of the bearing of the upper bearing cover.

[0089] In this embodiment, the pitch p of the to-be-designed spiral oil groove 3 is determined according to the existing design specification requirements; the determination process of the start angle γ1 and the end angle γ2 of the to-be-designed spiral oil groove is as follows:

[0090] Determine the rotation direction of the to-be-designed spiral oil groove 3 according to the rotation direction of the crankshaft in the compressor pump body.

[0091] Combined with the start and end angle Δγ of the to-be-designed spiral oil groove 3 and the layout area of the to-be-designed spiral oil groove 3 on the inner wall surface of the bearing, determine the start angle γ1 and the end angle γ2 of the to-be-designed spiral oil groove 3, so that the start point and the end point of the to-be-designed spiral oil groove 3 are both located in the layout area of the to-be-designed spiral oil groove 3 on the inner wall surface of the bearing.

[0092] Step 5: Compare the start and end angle Δγ of the to-be-designed spiral oil groove 3 with the layout area of the to-be-designed spiral oil groove 3 on the inner wall surface of the bearing. If the start and end angle Δγ of the to-be-designed spiral oil groove 3 is greater than the angle of the layout area of the to-be-designed spiral oil groove 3 on the inner wall surface of the bearing, move the start point of the to-be-designed spiral oil groove 3 towards the suction side of the compressor pump body by a preset distance to ensure that the end point of the to-be-designed spiral oil groove 3 is located in the layout area of the to-be-designed spiral oil groove on the inner wall surface of the bearing.

[0093] Design principle and design result:

[0094] In order to generate sufficient oil film thickness between the long shaft part and the short shaft part of the crankshaft and the upper bearing cap and the lower bearing cap, form effective lubrication, and play a role in support and friction reduction, lubricating oil needs to be provided on the crankshaft-bearing cap moving pair to generate sufficient oil film thickness; for this purpose, spiral oil grooves are designed on the inner wall surfaces of the bearing holes of the upper bearing cap and the lower bearing cap to strengthen the lubrication on the contact surfaces of the corresponding moving pairs.

[0095] Definition: The starting point of the crankshaft rotation angle is at the top dead center of the sliding vane 4. The crankshaft rotates counterclockwise. Taking the cylinder sliding vane groove as the reference point, the counterclockwise rotation direction of the crankshaft is the positive direction.

[0096] In the compressor pump body, a rotatable rolling piston 2 is sleeved on the outer circumferential surface of the eccentric part of the crankshaft; during the rotation of the crankshaft, the movement of the rolling piston 2 includes: rotating around the cylinder center at an angular velocity ω and rotating around its own center line at an angular velocity ω p ; among them, during the rotation of the rolling piston 2, the external forces acting on the rolling piston 2 include the gas force F acting on the rolling piston 2 g , the radial contact force F between the rolling piston 2 and the sliding vane 4 n , the tangential contact force F between the rolling piston 2 and the sliding vane 4 t and the rotational inertia force F of the rolling piston 2 1p , as shown in the appendix Figure 3 .

[0097] The action line of the resultant external force of all the resistances acting on the rolling piston 2 passes through the center of the rolling piston 2, constituting the load of the eccentric bearing; the magnitude of the resultant external force of all the resistances acting on the rolling piston 2 is related to the working medium, working conditions and the structure of the compressor pump body; and the direction of the resultant external force of all the resistances acting on the rolling piston 2 is mainly related to the structure of the compressor pump body; as shown in the appendix Figure 4 , the appendix Figure 4 gives the diagram of the change of the resultant external force direction acting on the rolling piston with the crankshaft rotation angle; it can be seen from the appendix Figure 4 that the acting direction of the resultant external force acting on the rolling piston is limited to the range of the inner wall surface of the bearing hole corresponding to the crankshaft rotation angle of 92° to 193°; as shown in the appendix Figure 5 , the appendix Figure 5 gives the diagram of the change of the resultant external force magnitude acting on the rolling piston with the crankshaft rotation angle; it can be seen from the appendix Figure 5 that the magnitude of the resultant external force acting on the rolling piston is between 170 and 1980 N; under different conditions, the trend of the change of the magnitude of the resultant external force acting on the rolling piston with the crankshaft rotation angle is the same.

[0098] During the gas compression process of the compressor pump body, it is necessary to overcome gas compression resistance, friction, etc. Its load first acts on the rolling piston, and then is transmitted to the eccentric part of the crankshaft, and then to the long shaft part and short shaft part of the crankshaft. Finally, it is borne by the upper bearing cover and the lower bearing cover. The force direction of the load is in the radial direction; the torque generated by the load is overcome by the driving torque generated by the motor, and the force generated by the load is balanced by the support reaction force of the upper bearing cover and the lower bearing cover; through the analysis of the load source, in order to balance the forces received by the crankshaft-rolling piston mechanism, the support reaction forces generated by the upper bearing cover and the lower bearing cover on the long shaft part and short shaft part of the crankshaft are exactly opposite to the direction of the force received by the rolling piston and equal in magnitude, satisfying the balance of force and torque; in the ideal state, the stress range of the upper bearing cover and the lower bearing cover is also limited to the wall surface range of the bearing inner hole corresponding to the crankshaft rotation angle of 92° to 193°; that is: in the case of one compression cycle during the compressor working cycle, the stress of the upper bearing cover and the lower bearing cover is limited to the wall surface range of the bearing inner hole corresponding to the crankshaft rotation angle of 92° to 193°, and other parts will not bear the force in the radial direction.

[0099] According to the fact that the stress of the upper bearing cover and the lower bearing cover is limited to the wall surface range of the bearing inner hole corresponding to the crankshaft rotation angle of 92° to 193°, and other areas of the wall surface of the bearing inner hole of the upper bearing cover and the lower bearing cover will not bear the force in the radial direction; therefore, the zero-pressure area of the bearing inner hole wall surface is: the wall surface area outside the stressed area of the bearing inner hole wall surface during the rotation of the crankshaft on the bearing inner hole wall surface, that is, the zero-pressure area of the bearing inner hole wall surface is the wall surface range of the bearing inner hole corresponding to the crankshaft rotation angle of -88° to 13°.

[0100] Compare the start-stop angle Δγ of the to-be-designed spiral oil groove with the layout area of the to-be-designed spiral oil groove on the bearing inner hole wall surface. If the start-stop angle Δγ of the to-be-designed spiral oil groove is greater than the angle of the layout area of the to-be-designed spiral oil groove on the bearing inner hole wall surface, that is, when the start-stop angle Δγ of the to-be-designed spiral oil groove exceeds the wall surface range of the bearing inner hole corresponding to the crankshaft rotation angle of -88° to 13°, move the starting point of the to-be-designed spiral oil groove a preset distance toward the suction side of the compressor pump body to ensure that the end point of the to-be-designed spiral oil groove is within the layout area of the to-be-designed spiral oil groove on the bearing inner hole wall surface; this can ensure lubrication while not having a significant impact on the surface wear and local stress of the moving pair.

[0101] From the appendix Figure 5 It can be seen that when the crankshaft rotation angle rotates from 0° to 57°, the magnitude of the force received hovers around 120N; and when the crankshaft rotation angle is greater than 57°, the magnitude of the force on the bearing inner hole wall surface increases rapidly until it reaches the peak value of 1980N at the 222° angle; then it rapidly decreases with the change of the rotation angle; therefore, the preset distance for moving the starting point of the to-be-designed spiral oil groove toward the suction side of the compressor pump body does not exceed the area of the bearing inner hole wall surface corresponding to the crankshaft rotation angle of 57°.

[0102] For the description of the relevant parts in a spiral oil groove design system, device, and computer-readable storage medium provided in this embodiment, reference can be made to the detailed description of the corresponding parts in a spiral oil groove design method described in this embodiment, which will not be repeated here.

[0103] The spiral oil groove design method of the present invention analyzes the forces on the rolling piston, takes the zero-pressure region of the inner wall surface of the bearing as the layout region for the spiral oil groove to be designed, avoids the wear of the spiral oil groove during the rotation of the crankshaft, ensures the reliability of the lubrication effect between the crankshaft-bearing cap moving pair, effectively reduces the power consumption of the crankshaft-bearing cap moving pair, and improves the reliability of the compressor pump body; provides a design basis for the design process of the spiral oil groove, and the design method is applicable to compressors in different refrigeration working medium usage occasions, different operating conditions, and different field application occasions; for example: air-conditioning refrigeration compressors, heat pump heating compressors, and refrigeration and cold storage compressors; and meets the design requirements for spiral oil grooves in compressors with different displacements.

[0104] The above embodiments are only one of the implementation manners capable of implementing the technical solution of the present invention. The scope of protection required by the present invention is not limited only by this embodiment, but also includes any changes, substitutions, and other implementation manners that are easily conceivable by those skilled in the art within the technical scope disclosed by the present invention.

Claims

1. A design method for a spiral oil groove, characterized in that, The described design method is used to determine the layout area of the spiral oil groove on the inner wall surface of the bearing of the upper bearing cover or the lower bearing cover of the compressor pump body; Among them, the described design method includes: According to the structural characteristics of the compressor pump body, perform a force analysis on the rolling piston to obtain the resultant external force of all the resistances acting on the rolling piston; According to the resultant external force of all the resistances acting on the rolling piston, determine the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft; According to the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft, obtain the zero-pressure-bearing area of the inner wall surface of the bearing, that is, obtain the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing; After obtaining the zero-pressure-bearing area of the inner wall surface of the bearing according to the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft, that is, obtaining the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing, it further includes a starting point correction step; Among them, the specific content of the starting point correction step is as follows: According to the height h of the inner bearing hole and the pitch p of the oil groove of the spiral oil groove to be designed, calculate the starting and ending angles Δγ of the spiral oil groove to be designed; Compare the starting and ending angles Δγ of the spiral oil groove to be designed with the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing. If the starting and ending angles Δγ of the spiral oil groove to be designed are greater than the angle of the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing, move the starting point of the spiral oil groove to be designed a preset distance towards the suction side of the compressor pump body to ensure that the ending point of the spiral oil groove to be designed is within the layout area of the spiral oil groove to be designed on the inner wall surface of the bearing; The process of determining the starting and ending angles Δγ of the spiral oil groove to be designed is specifically as follows: According to the height h of the inner bearing hole and the pitch p of the oil groove of the spiral oil groove to be designed, calculate the starting and ending angles Δγ of the spiral oil groove to be designed; The starting and ending angles Δγ of the spiral oil groove to be designed are:

2. The design method of a spiral oil groove according to claim 1, characterized in that, All the resistances acting on the rolling piston include: the gas force F acting on the rolling piston g , the radial contact force F between the rolling piston and the sliding vane n , the tangential contact force F between the rolling piston and the sliding vane t and the rotational inertia force F of the rolling piston 1p .

3. A design method for a spiral oil groove according to claim 1, characterized in that, The process of determining the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston is specifically as follows: According to the resultant external force of all the resistances acting on the rolling piston, determine the direction of the resultant external force acting on the rolling piston; According to the direction of the resultant external force acting on the rolling piston, determine the pressure-bearing range of the inner wall surface of the bearing during the rotation of the crankshaft, that is, obtain the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft.

4. A spiral oil groove design method according to claim 1, characterized in that The zero-pressure-bearing area of the inner wall surface of the bearing is: on the inner wall surface of the bearing, the wall surface area outside the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft.

5. A spiral oil groove design system, characterized in that, The described design system is used to determine the layout area of the spiral oil groove on the inner wall surface of the bearing of the upper bearing cover or the lower bearing cover of the compressor pump body; Among them, the described design system includes: A force analysis module, which is used to perform a force analysis on the rolling piston according to the structural characteristics of the compressor pump body to obtain the resultant external force of all the resistances acting on the rolling piston; A pressure-bearing area determination module, which is used to determine the pressure-bearing area of the inner wall surface of the bearing during the rotation of the crankshaft according to the resultant external force of all the resistances acting on the rolling piston; The layout area determination module is used to obtain the zero-pressure area of the inner hole wall of the bearing according to the pressure-bearing area of the inner hole wall of the bearing during the rotation of the crankshaft, that is, to obtain the layout area of the to-be-designed spiral oil groove on the inner hole wall of the bearing; After obtaining the zero-pressure area of the inner hole wall of the bearing according to the pressure-bearing area of the inner hole wall of the bearing during the rotation of the crankshaft, that is, obtaining the layout area of the to-be-designed spiral oil groove on the inner hole wall of the bearing, it further includes a starting point correction step; Among them, the starting point correction step is specifically as follows: According to the height h of the inner hole of the bearing and the pitch p of the to-be-designed spiral oil groove, calculate the start-stop angle Δγ of the to-be-designed spiral oil groove; Compare the start-stop angle Δγ of the to-be-designed spiral oil groove with the layout area of the to-be-designed spiral oil groove on the inner hole wall of the bearing. If the start-stop angle Δγ of the to-be-designed spiral oil groove is greater than the angle of the layout area of the to-be-designed spiral oil groove on the inner hole wall of the bearing, move the starting point of the to-be-designed spiral oil groove a preset distance towards the suction side of the compressor pump body to ensure that the end point of the to-be-designed spiral oil groove is within the layout area of the to-be-designed spiral oil groove on the inner hole wall of the bearing; The process of determining the start-stop angle Δγ of the to-be-designed spiral oil groove is specifically as follows: According to the height h of the inner hole of the bearing and the pitch p of the to-be-designed spiral oil groove, calculate the start-stop angle Δγ of the to-be-designed spiral oil groove; The start-stop angle Δγ of the to-be-designed spiral oil groove is:

6. A spiral oil groove design device, characterized in that, Including: A memory for storing computer programs; A processor for implementing the steps of the spiral oil groove design method according to any one of claims 1-4 when executing the computer program.

7. A computer-readable storage medium storing a computer program, characterized in that, The computer program, when executed by the processor, implements the steps of the spiral oil groove design method according to any one of claims 1-4.

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