Generator crankshaft design method, device and equipment and storage medium

Abstract

The invention discloses a generator crankshaft design method, device and equipment and a storage medium, the method comprises the steps that a crankshaft three-dimensional model meeting preset crankshaft design requirements is obtained, and the preset crankshaft design requirements comprise structure parameters of a piston, a connecting rod neck and an air cylinder and whole machine performance characteristic parameters; determining a counterweight permutation combination based on the crankshaft three-dimensional model, wherein the counterweight permutation combination comprises the structures, the number and the arrangement positions of counterweights; calculating the balance rate of each counterweight permutation combination, and screening from each counterweight permutation combination according to the balance rate to obtain a candidate counterweight permutation combination; detecting whether the characteristic parameters of the crankshaft provided with the candidate counterweight permutation and combination meet preset index requirements or not; and determining the candidate counterweight permutation and combination corresponding to the crankshaft of which the characteristic parameters meet a preset index requirement as a preferred counterweight permutation and combination. Reasonability of counterweight structure arrangement is achieved, and shafting balance is improved.

Description

TECHNICAL FIELD

[0001] The embodiment of the present application relates to the technical field of a generator crankshaft, in particular to a generator crankshaft design method, device, equipment and storage medium. BACKGROUND

[0002] The crankshaft is a key component in a generator or an internal combustion engine, which converts the reciprocating motion of the piston into rotary motion. Since the crankshaft generates additional centrifugal inertia force, reciprocating inertia force and force couple during operation, the effects of these forces and couples will adversely affect the operation reliability and service life of the diesel internal combustion engine or the generator, which will cause the friction pair to wear out, the operating noise to increase, the whole machine vibration to increase, and even cause the failure of the internal combustion engine parts, thereby affecting the reliability of the whole machine set. Therefore, it is often necessary to set a balance weight on the crankshaft to ensure the balance of the crankshaft shafting, but in the prior art, there is no design scheme for the arrangement and combination of the balance weight on the crankshaft, and the structural arrangement of the balance weight is mostly determined by the experience of engineers, which leads to the fact that the balance of the shafting cannot be ensured, the whole machine vibration caused by the crankshaft cannot be effectively reduced, and the technical problems such as the wear of the friction pair and the increase of the operating noise still exist. SUMMARY

[0003] The purpose of the present application is to at least provide a generator crankshaft design method, device, equipment and storage medium, which can at least solve the technical problem that the inertia force and torque generated during operation affect the reliability of the mine diesel generator set in the prior art.

[0004] To solve the above technical problems, at least one embodiment of the present application provides a generator crankshaft design method, comprising: obtaining a crankshaft three-dimensional model satisfying a preset crankshaft design requirement, wherein the preset crankshaft design requirement includes structural parameters of a piston, a connecting rod neck and a cylinder, and whole machine performance characteristic parameters; determining a balance weight arrangement combination based on the crankshaft three-dimensional model, wherein the balance weight arrangement combination includes the structure, number and arrangement position of the balance weight; calculating the balance rate of each balance weight arrangement combination, and selecting a candidate balance weight arrangement combination from each balance weight arrangement combination according to the balance rate; detecting whether the characteristic parameters of the crankshaft arranged with the candidate balance weight arrangement combination meet the preset index requirement; determining that the candidate balance weight arrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirement is an optimal balance weight arrangement combination.

[0005] At least one embodiment of the present application also provides a generator crankshaft design device, comprising: The acquisition module is configured to acquire a three-dimensional model of a crankshaft that meets preset crankshaft design requirements, the preset crankshaft design requirements including structural parameters of a piston, a connecting rod neck, and a cylinder, and whole-machine performance characteristic parameters. The arrangement combination determination module is configured to determine a balance weight arrangement combination based on the three-dimensional model of the crankshaft, the balance weight arrangement combination including a balance weight structure, a balance weight number, and an arrangement position. The balance rate calculation module is configured to calculate a balance rate of each balance weight arrangement combination, and to select a candidate balance weight arrangement combination from each balance weight arrangement combination according to the balance rate. The detection module is configured to detect whether a characteristic parameter of a crankshaft arranged with the candidate balance weight arrangement combination meets preset index requirements. The preferred module is configured to determine that the candidate balance weight arrangement combination corresponding to the crankshaft whose characteristic parameter meets preset index requirements is a preferred balance weight arrangement combination.

[0006] At least one embodiment of the present application also provides an electronic device, including at least one processor, and a memory connected with the at least one processor in communication; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to perform the generator crankshaft design method described above.

[0007] At least one embodiment of the present application also provides a computer-readable storage medium storing a computer program, and the computer program is executed by a processor to implement the generator crankshaft design method described above.

[0008] The generator crankshaft design method, device, electronic device, and computer-readable storage medium provided by the embodiments of the present application achieve the rationality of balance weight structure arrangement, improve shafting balance, effectively reduce generator whole-machine vibration caused by a crankshaft system, and further effectively improve the reliability of a generator set, by calculating balance rates of each balance weight arrangement combination, selecting a better candidate balance weight arrangement combination therefrom, detecting whether a characteristic parameter of a crankshaft arranged with the candidate balance weight arrangement combination meets preset index requirements, and determining that the candidate balance weight arrangement combination corresponding to the crankshaft whose characteristic parameter meets preset index requirements is a preferred balance weight arrangement combination.

[0009] In some optional embodiments, the step of calculating balance rates of each balance weight arrangement combination, and selecting a candidate balance weight arrangement combination from each balance weight arrangement combination according to the balance rates includes: calculating a first combined unbalanced torque when there is no balance weight, and a second combined unbalanced torque under each balance weight arrangement combination based on the three-dimensional model of the crankshaft; determining a balance rate of each of the balance weight arrangement combinations based on the first and second combined unbalance moments; screening a candidate balance weight arrangement combination from each of the balance weight arrangement combinations according to the balance rate.

[0010] In some optional embodiments, the step of calculating the first combined unbalance moment without balance weight and the second combined unbalance moment under each of the balance weight arrangement combinations based on the three-dimensional model of the crankshaft comprises: obtaining a shafting horizontal direction unbalance moment and a shafting vertical direction unbalance moment of the crankshaft without balance weight; determining the first combined unbalance moment based on the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft without balance weight; obtaining a shafting horizontal direction unbalance moment and a shafting vertical direction unbalance moment of the crankshaft under each of the balance weight arrangement combinations; determining the second combined unbalance moment based on the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft under each of the balance weight arrangement combinations.

[0011] In some optional embodiments, the expression of the shafting horizontal direction unbalance moment is: = maRw2[ sin(Φ+ )+ sin(Φ+ )+...+ sin(Φ+ )]; the expression of the shafting vertical direction unbalance moment is: = maRw2[ cos(Φ+ )+ cos(Φ+ )+...+ cos(Φ+ )]; the expression of the shafting combined unbalance moment is: ΣM=

[0012] wherein, is the shafting horizontal direction unbalance moment, is the shafting horizontal direction unbalance moment, ΣM is the shafting horizontal direction unbalance moment, Φ is the included angle between the first crank and the vertical center line, Z is the number of cylinders (the number of cranks), , ... is the included angle between each crank and the first crank, 、 ... is the distance between each cylinder (connecting rod journal) center line and the vertical center line of the crankshaft center journal.

[0013] In some optional embodiments, the expression of the balance rate is: P=

[0014] wherein P is the balance rate, is the first synthesized unbalanced moment calculated when the shafting has no balance weight, is the second synthesized unbalanced moment calculated when the shafting has different balance weight arrangement schemes.

[0015] In some optional embodiments, the characteristic parameters include torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency, and oil film thickness.

[0016] In some optional embodiments, the step of obtaining the three-dimensional model of the crankshaft satisfying the preset crankshaft design requirements, the preset crankshaft design requirements including the structural parameters of the piston, the connecting rod journal, and the cylinder, and the whole machine performance characteristic parameters, includes: obtaining the preset crankshaft design requirements, the preset crankshaft design requirements including the structural parameters of the piston, the connecting rod journal, and the cylinder, and the whole machine performance characteristic parameters; determining the crankshaft system firing order and the structural size index according to the preset crankshaft design requirements; constructing the three-dimensional model of the crankshaft according to the crankshaft system firing order and the structural size index. BRIEF DESCRIPTION OF DRAWINGS

[0017] One or more embodiments are illustrated by way of example in the figures that form a part of this patent document. These example are not intended to limit the implementation of the embodiments.

[0018] Figure 1 a flowchart of a generator crankshaft design method provided by one embodiment of the present application; Figure 2 a flowchart of a generator crankshaft design method provided by another embodiment of the present application; Figure 3 a crankshaft diagram based on the generator crankshaft design method provided by another embodiment of the present application; Figure 4 a balance block structure diagram based on the generator crankshaft design method provided by another embodiment of the present application; Figure 5 a schematic diagram of a generator crankshaft design device provided by another embodiment of the present application; Figure 6 A structural schematic diagram of an electronic device is provided for another embodiment of the present application.

[0019] In the drawings, the same components are designated by the same reference numerals, and the drawings are not drawn to scale. DETAILED DESCRIPTION

[0020] To make the objectives, technical solutions and advantages of the embodiments of the present application clearer, the embodiments of the present application will be described in detail below with reference to the drawings. However, those skilled in the art can understand that, in the embodiments of the present application, many technical details are presented in order to make the readers better understand the present application. However, the technical solutions claimed by the present application can be implemented even without these technical details and various changes and modifications based on the following embodiments. The division of the following embodiments is for the convenience of description, and should not constitute any limitation on the specific implementation of the present application, and the embodiments can be combined with each other and quoted to each other without contradiction.

[0021] It should be noted that the terms “first”, “second”, and the like in the specification and claims of the present disclosure and the above drawings are used to distinguish similar objects, and do not necessarily have to be used to describe a specific order or sequence. It should be understood that the data thus used can be interchanged under appropriate circumstances, so that the embodiments of the present disclosure described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms “include” and “have” and any variations thereof are intended to cover non-exclusive inclusion, for example, a process, method, system, product or device including a series of steps or units does not have to be limited to only those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0022] It should be noted that the steps shown in the flowchart of the drawings can be executed in a computer system such as a set of computer executable instructions, and although a logical order is shown in the flowchart, in some cases, the steps shown or described herein can be executed in an order different from that described herein.

[0023] Embodiment one: Figure 1 A flowchart of a generator crankshaft design method is provided for an embodiment of the present disclosure. As shown in the figure, Figure 1 The generator crankshaft design method comprises: Step 110, obtaining a crankshaft three-dimensional model satisfying a preset crankshaft design requirement, wherein the preset crankshaft design requirement comprises structural parameters of a piston, a connecting rod neck and a cylinder, and whole machine performance characteristic parameters.

[0024] Specifically, based on the preset crankshaft design requirements, the modeling parameters are parameterized, and the three-dimensional model of the crankshaft is obtained based on the modeling parameters.

[0025] In one example, the preset crankshaft design requirements include structural parameters of the piston, the connecting rod neck and the cylinder, and performance characteristic parameters of the whole machine. Further, the crankshaft firing order and the structural size index are determined according to the preset crankshaft design requirements, and the crank angle is determined according to the cylinder arrangement and the ignition order, so as to determine the modeling parameters of the crankshaft, and establish the three-dimensional model in the three-dimensional software based on the modeling parameters of the crankshaft.

[0026] In step 120, the balance weight arrangement combination is determined based on the three-dimensional model of the crankshaft, and the balance weight arrangement combination includes the structure, the number and the arrangement position of the balance weight.

[0027] Specifically, based on the three-dimensional model of the crankshaft, the centrifugal inertia force, the reciprocating inertia force and the force couple generated by the generator during operation are determined, and a plurality of balance weight arrangement combinations are determined, the balance weight arrangement combination including the structure, the number and the arrangement position of the balance weight, wherein the structure and / or the number and / or the arrangement position of the balance weight of each balance weight arrangement combination are different.

[0028] In step 130, the balance rate of each balance weight arrangement combination is calculated, and the candidate balance weight arrangement combination is selected from each balance weight arrangement combination according to the balance rate.

[0029] Specifically, the generator will generate additional centrifugal inertia force, reciprocating inertia force and force couple during operation, and the action of these forces and couples will have adverse effects on the operation reliability and service life of the diesel internal combustion engine, will cause the friction pair to wear out, the operation noise to increase, the whole machine vibration to increase, and even cause the failure of the internal combustion engine parts, and further affect the reliability of the generator set. In order to effectively reduce the whole machine vibration caused by the crankshaft system, the balance weight needs to be reasonably designed and arranged to improve the balance of the shaft system. The rationality of the balance weight structure arrangement is characterized by the balance rate. Further, the rationality of each balance weight arrangement combination is evaluated by calculating the balance rate of each balance weight arrangement combination, and the balance weight arrangement combination with better balance rate is selected from all balance weight arrangement combinations to determine the candidate balance weight arrangement combination.

[0030] In step 140, it is detected whether the characteristic parameters of the crankshaft arranged with the candidate balance weight arrangement combination meet the preset index requirements.

[0031] Specifically, on the basis of meeting the balance rate requirements, the characteristic parameters of the crankshaft arranged with the candidate balance weight arrangement combination need to be checked to further realize the optimization of the crankshaft structure. Step 150, determining that the candidate balance rearrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirement is the preferred balance rearrangement combination.

[0032] Specifically, when the characteristic parameters of the crankshaft arranged with the candidate balance rearrangement combination meet the preset index requirement, it is determined that the corresponding candidate balance rearrangement combination is the preferred balance rearrangement combination; when the characteristic parameters of the crankshaft arranged with the candidate balance rearrangement combination do not meet the preset index requirement, the balance rearrangement combination is re-determined based on the three-dimensional model of the crankshaft until a balance rearrangement combination meeting the preset index requirement is output.

[0033] In this embodiment, the balance rates of each balance rearrangement combination are calculated, and the better candidate balance rearrangement combination is screened from them, and on this basis, it is detected whether the characteristic parameters of the crankshaft arranged with the candidate balance rearrangement combination meet the preset index requirement, and it is determined that the candidate balance rearrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirement is the preferred balance rearrangement combination, so as to realize the rationality of the balance structure arrangement, improve the balance of the shaft system, effectively reduce the vibration of the generator caused by the crankshaft system, and further effectively improve the reliability of the generator set.

[0034] In some embodiments, the step of calculating the balance rate of each balance rearrangement combination and screening the candidate balance rearrangement combination from each balance rearrangement combination according to the balance rate comprises: calculating a first combined unbalanced torque when there is no balance weight and a second combined unbalanced torque under each balance rearrangement combination based on the three-dimensional model of the crankshaft; determining the balance rate of each balance rearrangement combination based on the first combined unbalanced torque and the second combined unbalanced torque; screening the candidate balance rearrangement combination from each balance rearrangement combination according to the balance rate.

[0035] Specifically, the balance rate is a key index for measuring the rotation stability of the crankshaft, and the balance rate directly affects the vibration, noise and service life of the engine. If the balance rate is not up to standard, the crankshaft will generate excessive centrifugal force when rotating efficiently, resulting in bearing wear, cylinder vibration and even crankshaft fracture. Further, the balance rate refers to the ratio of the remaining unbalance after balancing to the allowable value.

[0036] In one example, the first combined unbalanced torque when there is no balance weight and the second combined unbalanced torque under each balance rearrangement combination are calculated, and the balance rate of each balance rearrangement combination is determined based on the first combined unbalanced torque and the second combined unbalanced torque.

[0037] In some embodiments, the step of calculating the first resultant unbalance moment without counterweight and the second resultant unbalance moment under each counterweight arrangement based on the three-dimensional model of the crankshaft comprises: obtaining the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft without counterweight; determining the first resultant unbalance moment based on the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft without counterweight; obtaining the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft under each counterweight arrangement; determining the second resultant unbalance moment based on the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft under each counterweight arrangement.

[0038] In some embodiments, the expression of the shafting horizontal direction unbalance moment is: = maRw2[ sin(Φ ) + sin(Φ ) +... + sin(Φ )] ; the expression of the shafting vertical direction unbalance moment is: = maRw2[ cos(Φ ) + cos(Φ ) +... + cos(Φ )] ; the expression of the shafting resultant unbalance moment is: ΣM=

[0039] wherein, is the shafting horizontal direction unbalance moment, is the shafting horizontal direction unbalance moment, ΣM is the shafting horizontal direction unbalance moment, Φ is the included angle between the first crank and the vertical center line, Z is the number of cylinders (number of cranks), , ... is the included angle between each crank and the first crank, , ... is the distance between the center line of each cylinder (connecting rod neck) and the vertical center line of the crankshaft center shaft neck.

[0040] Specifically, the shaft system horizontal direction and vertical direction unbalanced moment are calculated respectively, and coupled as a combined unbalanced moment, and the balance rate of the balance weight arrangement combination is determined based on the combined unbalanced moment calculated when the shaft system has no balance weight and the combined unbalanced moment calculated when the shaft system has different balance weight arrangement combinations.

[0041] In some embodiments, the expression of the balance rate is: P=

[0042] Wherein, P is the balance rate, is the first combined unbalanced moment calculated when the shaft system has no balance weight, is the second combined unbalanced moment calculated when the shaft system has different balance weight arrangement schemes.

[0043] In some embodiments, the characteristic parameters include torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency and oil film thickness.

[0044] Specifically, after obtaining the candidate balance weight arrangement combinations, it is detected whether the characteristic parameters of the crankshaft arranged with any candidate balance weight arrangement combination meet the preset index requirements, wherein the characteristic parameters include torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency and oil film thickness, and through detecting whether the above characteristic parameters meet the preset index requirements, the candidate balance weight arrangement combinations are further screened to ensure the rationality of the structure arrangement of the selected optimal balance weight arrangement combination.

[0045] In some embodiments, the step of obtaining the three-dimensional model of the crankshaft meeting the preset crankshaft design requirements includes: obtaining the preset crankshaft design requirements, wherein the preset crankshaft design requirements include the structural parameters of the piston, the connecting rod neck and the cylinder, and the performance characteristic parameters of the whole machine; determining the crankshaft system firing order and the structure size index according to the preset crankshaft design requirements; constructing the three-dimensional model of the crankshaft according to the crankshaft system firing order and the structure size index.

[0046] Specifically, the preset crankshaft design requirements include the structural parameters of the piston, the connecting rod neck and the cylinder, and the performance characteristic parameters of the whole machine, the crankshaft system firing order and the structure size index are determined according to the preset crankshaft design requirements, and the crank angle is determined according to the cylinder arrangement and the ignition order, so as to determine the modeling parameters of the crankshaft, and the three-dimensional model is established in the three-dimensional software based on the modeling parameters of the crankshaft.

[0047] In the embodiment, the balance rate of each balance rearrangement combination is calculated, and a better candidate balance rearrangement combination is screened from the balance rate, and on the basis of the candidate balance rearrangement combination, whether the characteristic parameter of the crankshaft arranged with the candidate balance rearrangement combination meets the preset index requirement is detected, the candidate balance rearrangement combination corresponding to the crankshaft whose characteristic parameter meets the preset index requirement is determined as the preferred balance rearrangement combination, so that the rationality of the balance rearrangement structure arrangement is realized, the shafting balance is improved, the vibration of the whole generator caused by the crankshaft is effectively reduced, and the reliability of the generator set is effectively improved.

[0048] Embodiment two: Another embodiment of the present application relates to a design method of a crankshaft, referring to Figure 2 The design method of the crankshaft comprises the following steps: Step 1: determining the design input of a diesel generator crankshaft; Step 2: determining the crankshaft system firing order and structure size index according to the input of step 1; Step 3: establishing a three-dimensional model in a three-dimensional software based on the size index given in step 2; Step 4: designing a balance rate calculation tool based on the shafting unbalanced moment formula and the three-dimensional model in step 3 by EXCEL; Step 5: determining a better crankshaft balance weight structure and arrangement method according to the tool given in step 4; Step 6: checking the result obtained in step 5 for the shafting and comparing the checking result with the allowable value; Step 7: if the checking result in step 6 meets the requirement, the result is output, if the checking result does not meet the requirement, the balance weight is optimized and designed, and steps 3 to 5 are repeated until the corresponding checking result meets the requirement and the corresponding crankshaft balance weight structure and arrangement method are output.

[0049] Further, step 4: the step of designing a balance rate calculation tool based on the shafting unbalanced moment formula and the three-dimensional model in step 3 by EXCEL comprises: S41: calculating the shafting horizontal and vertical direction unbalanced moments respectively, coupling them into a resultant moment, and converting them into a balance rate; S42: verifying the accuracy of the S41 model by using a mature example; In step 41, the horizontal and vertical direction unbalanced moment, the resultant moment and the balance rate calculation formula are as follows: Shafting horizontal direction unbalanced moment: ΣM1X= maRw2[L1sin(Φ+θ1)+ L2 sin(Φ+θ2)+...+Lzsin(Φ+θz)] Sum of vertical unbalance moment of shafting:∑M1y=maRw2[L1cos(Φ+θ1)+L2cos(Φ+θ2)+...+Lzcos(Φ+θz)] Balance rate: P=

[0050] In the formula, Φ is the included angle between the first crank and the vertical center line, Z is the number of cylinders (the number of cranks), θ1, θ2... θz are the included angles between each crank and the first crank, L1, L2... Lz are the distances between the center line of each cylinder (the neck of the connecting rod) and the vertical center line of the center shaft neck of the crankshaft, is the calculated combined unbalance moment of the shafting without balancing weight, is the calculated combined unbalance moment of the shafting under different balancing weight arrangement schemes.

[0051] Further, step 1: determining the design input of the diesel generator crankshaft includes the design structure of the crankshaft scheme, the overall performance characteristic parameters, the performance and structure parameters of the piston, the connecting rod and the cylinder liner.

[0052] Further, step 5: the step of determining the optimal crankshaft balancing weight structure and arrangement method according to the tool given in step 4 includes: According to the arrangement combination, the balancing weight arrangement schemes for the crankshaft are listed, and the balance rates of the shafting under different schemes are calculated, and the optimal result is selected from each scheme for the checking calculation of step 6.

[0053] Further, in step 6, the shafting parameters determined in step 5 are respectively evaluated by calculation, including the torsional vibration amplitude, bearing lubrication, torsional stress, natural frequency and oil film thickness of the shafting scheme determined in step 4.

[0054] Further, the results obtained in step 6 are compared with the allowable values, and if the requirements are not met, the structure of the balancing weight is optimized.

[0055] The design method of the generator crankshaft provided in the embodiment, by calculating the balance rates of each balancing weight arrangement combination, the optimal candidate balancing weight arrangement combination is screened, and on the basis thereof, it is detected whether the characteristic parameters of the crankshaft arranged with the candidate balancing weight arrangement combination meet the preset index requirements, the candidate balancing weight arrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirements is the optimal balancing weight arrangement combination, so as to realize the rationality of the balancing weight structure arrangement, improve the balance of the shafting, effectively reduce the vibration of the generator caused by the crankshaft system, and further effectively improve the reliability of the generator set.

[0056] Example Three: Another embodiment of the present application relates to a design method of a crankshaft, which is applied to a 16-cylinder V-type mine diesel generator. In the mine truck, the power scheme of electric propulsion is mostly used, and the diesel engine is often used as the power source of the motor. The 16-cylinder V-type diesel generator is a commonly used generator type. According to the structural characteristics of the diesel engine room of the mine truck, the diesel engine will adopt a three-point support mode. In order to ensure the reliability of the generator set and the diesel engine in operation, it is necessary to minimize the vibration generated by the diesel engine itself. The 16V diesel engine crankshaft is not mirror-symmetric, which will generate additional centrifugal inertia force, reciprocating inertia force and force couple during operation. The action of these forces and couples will have an adverse effect on the operation reliability and service life of the diesel engine, will cause the friction pair to wear out, the operation noise to increase, and the whole machine vibration to increase, and in severe cases, it will even cause the failure of the internal combustion engine parts, and further affect the reliability of the mine diesel generator set. Based on this, the present embodiment discloses a design method of a crankshaft to reduce the vibration and wear problems that are prone to occur during the operation of the above mine diesel generator. The method comprises the following steps: Step 1: determining the design input of the diesel generator crankshaft; Step 2: determining the crankshaft system firing sequence and structure size index according to the input of step 1; Step 3: establishing a three-dimensional model in a three-dimensional software based on the size index given in step 2; Step 4: designing a balance rate calculation tool based on the shaft unbalance torque formula and the three-dimensional model in step 3 through EXCEL; Step 5: determining the optimal crankshaft counterweight structure and arrangement method according to the tool given in step 4; Step 6: checking the result obtained in step 5 for the shaft system and comparing the checking result with the allowable value; Step 7: if the checking result in step 6 meets the requirements, the result is output, if it does not meet the requirements, the counterweight is optimized and designed, and steps 3 to 5 are repeated until the corresponding checking result meets the requirements and the corresponding crankshaft counterweight structure and arrangement method are output.

[0057] Further, step 4: the step of designing a balance rate calculation tool based on the shaft unbalance torque formula and the three-dimensional model in step 3 through EXCEL comprises: S41: calculating the shaft unbalance torque in the horizontal and vertical directions respectively, coupling them into a resultant torque, and converting them into a balance rate; S42: verifying the accuracy of the S41 model using mature examples; In step 41, the calculation formulas of the horizontal and vertical unbalance torques, the resultant torque and the balance rate are as follows: Sum of horizontal unbalance moment of shafting:∑M1X=maRw2[L1sin(Φ+θ1)+L2sin(Φ+θ2)+...+Lzsin(Φ+θz)] Sum of vertical unbalance moment of shafting:∑M1Y=maRw2[L1cos(Φ+θ1)+L2cos(Φ+θ2)+...+Lzcos(Φ+θz)] Balance ratio: P=∑M1X / ∑M1Y

[0058] Wherein: Φ is the angle between the first crank and the vertical center line, Z is the number of cylinders (crank number), θ1, θ2... θz is the angle between each crank and the first crank, L1, L2... Lz is the distance between the center line of each cylinder (connecting rod neck) and the vertical center line of the crankshaft center journal, is the calculated combined unbalance moment of the shafting without balance weight, is the calculated combined unbalance moment of the shafting under different balance weight arrangement schemes.

[0059] Further, step 1: determining the design input of the diesel generator crankshaft includes the design structure of the crankshaft scheme, the overall performance characteristic parameters, the performance and structure parameters of the piston, connecting rod and cylinder liner.

[0060] Further, step 5: the step of determining the optimal crankshaft balance weight structure and arrangement method according to the tool given in step 4 includes: This embodiment takes a 16-cylinder V-type crankshaft of a diesel generator as an example for illustration, enumerates the balance weight arrangement schemes for the 16-cylinder V-type crankshaft according to permutation and combination, and calculates the balance ratio of the shafting under different schemes, and selects the optimal result from each scheme for the checking calculation of step 6.

[0061] Further, in step 6, the shafting parameters determined in step 5 are respectively evaluated by calculation to evaluate the torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency and oil film thickness under the shafting scheme determined in step 4.

[0062] Further, the results obtained in step 6 are compared with the allowable values, and if the requirements are not met, the structure of the balance weight is optimized.

[0063] Referring to Figure 3 as shown, Figure 3The crankshaft structural arrangement scheme generated by the design method of the crankshaft based on the embodiment; specifically, the crankshaft structural arrangement scheme includes a crankshaft set (1), a balance block (2), the crankshaft set (1) contains a main journal (1.1), a crank arm (1.2), a connecting rod journal (1.3), a timing gear (1.4), an output flange (1.5), the main journal (1.1) is composed of a first main journal (1.1.1), a second main journal (1.1.2) and a third main journal (1.1.3), the crank arm (1.2) is correspondingly arranged at both ends of the connecting rod journal (1.3), the first main journal (1.1.1) is arranged between the output flange (1.5) and the first crank arm (1.2) on the A side, the third main journal (1.1.3) is arranged between the timing gear (1.4) and the first crank arm (1.2) on the B side, the remaining main journals are all second main journals (1.1.2), the balance block (2) is arranged on the remaining crank arms except the fourth and fifth crank arms (1.2) on the A side and the fourth and fifth crank arms (1.2) on the B side, the crankshaft set (1) contains only 12 balance blocks (2), wherein the balance block (2) includes a mass in the range of 1600 grams to 2000 grams, preferably 1800 grams.

[0064] Continuing to refer to Figure 4 As shown, the specific dimensions of the balance block include a balance weight radius (R), a balance weight thickness (D), a balance weight revolution radius (RR) and a balance weight unbalance amount (WR), the term balance weight unbalance amount (WR) is defined as the product of the mass of the balance weight and the measured balance weight revolution radius (RR), the balance weight radius (R) is contained between 208 millimeters (208mm) and 210 millimeters (210mm), preferably 209 millimeters (209mm), the balance weight thickness (D) is contained between 54 millimeters (54mm) and 56 millimeters (56mm), preferably 55 millimeters (55mm), the balance weight revolution radius (RR) is between 112 millimeters (112mm) and 114 millimeters (114mm), preferably 113 millimeters (113mm), and the balance weight unbalance amount (WR) is included in the range of 2100 kilogram-millimeters (2100Kgmm) to 2200 kilogram-millimeters (2200Kgmm), preferably 2120 kilogram-millimeters (2120Kgmm).

[0065] The additional vibration of the crankshaft system in this state due to rotation will be greatly reduced, and the overall vibration of the diesel engine will also be greatly reduced, greatly improving the reliability of the mine diesel generator.

[0066] The design method provided by the embodiment based on the crankshaft of the 16-cylinder V-type mine diesel generator, the balance rate of each balance weight arrangement combination is calculated, the better candidate balance weight arrangement combination is screened from the balance weight arrangement combinations, and whether the characteristic parameters of the crankshaft arranged with the candidate balance weight arrangement combination meet the preset index requirements is detected on the basis of the candidate balance weight arrangement combination. The candidate balance weight arrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirements is the preferred balance weight arrangement combination. In this way, the rationality of the balance weight arrangement is realized, the balance of the shaft system is improved, the vibration of the generator caused by the crankshaft system is effectively reduced, and the reliability of the generator set is effectively improved.

[0067] Embodiment four Another embodiment of the present application relates to a generator crankshaft design device. The implementation details of the generator crankshaft design device of the embodiment are specifically described as follows. The following implementation details are provided for the convenience of understanding and are not essential for implementing the present solution. The schematic diagram of the generator crankshaft design device of the embodiment can be as shown in Figure 5 The generator crankshaft design device of the embodiment includes an acquisition module 501, an arrangement combination determination module 502, a balance rate calculation module 503, a detection module 504, and a preferred module 505.

[0068] The acquisition module 501 is configured to acquire a crankshaft three-dimensional model that meets preset crankshaft design requirements. The preset crankshaft design requirements include the structural parameters of pistons, connecting rod necks, and cylinders, and the performance characteristic parameters of the whole machine. The arrangement combination determination module 502 is configured to determine a balance weight arrangement combination based on the crankshaft three-dimensional model. The balance weight arrangement combination includes the structure, number, and arrangement position of the balance weight. The balance rate calculation module 503 is configured to calculate the balance rate of each balance weight arrangement combination and screen a candidate balance weight arrangement combination from each balance weight arrangement combination according to the balance rate. The detection module 504 is configured to detect whether the characteristic parameters of the crankshaft arranged with the candidate balance weight arrangement combination meet the preset index requirements. The preferred module 505 is configured to determine that the candidate balance weight arrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirements is a preferred balance weight arrangement combination.

[0069] In some optional embodiments, the balance rate calculation module 503 is further configured to calculate a first synthesized unbalanced torque when there is no balance weight and a second synthesized unbalanced torque under each balance weight arrangement combination based on the crankshaft three-dimensional model. The balance rate of each balance weight arrangement combination is determined based on the first synthesized unbalanced torque and the second synthesized unbalanced torque. The candidate balance weight arrangement combination is screened from each balance weight arrangement combination according to the balance rate.

[0070] In some optional embodiments, the balance rate calculation module 503 is further configured to obtain the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft without the counterweight; determine the first combined unbalance moment based on the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft without the counterweight; obtain the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft under each of the counterweight arrangement combinations; determine the second combined unbalance moment based on the shafting horizontal direction unbalance moment and the shafting vertical direction unbalance moment of the crankshaft under the counterweight arrangement combinations.

[0071] In some optional embodiments, the expression of the shafting horizontal direction unbalance moment is: = maRw2[ sin(Φ ) + sin(Φ ) +... + sin(Φ )] ; The expression of the shafting vertical direction unbalance moment is: = maRw2[ cos(Φ ) + cos(Φ ) +... + cos(Φ )] ; The expression of the shafting combined unbalance moment is: ΣM=

[0072] wherein, is the shafting horizontal direction unbalance moment, is the shafting horizontal direction unbalance moment, ΣM is the shafting horizontal direction unbalance moment, Φ is the included angle between the first crank and the vertical center line, Z is the number of cylinders (the number of cranks), , ... is the included angle between each crank and the first crank, , ... is the distance between the center line of each cylinder (the big end of the connecting rod) and the vertical center line of the center shaft neck of the crankshaft.

[0073] In some optional embodiments, the expression of the balance rate is: P=

[0074] wherein P is the balance rate, is a first synthesized unbalanced moment calculated when the shaft system has no balance weight, is a second synthesized unbalanced moment calculated when the shaft system has different balance weight arrangement.

[0075] In some optional embodiments, the characteristic parameters include torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency, and oil film thickness.

[0076] In some optional embodiments, the acquisition module 501 is further configured to acquire a preset crankshaft design requirement, the preset crankshaft design requirement including structural parameters of a piston, a connecting rod neck, and a cylinder, and whole machine performance characteristic parameters. determine a crankshaft system firing order and a structural size index according to the preset crankshaft design requirement; construct a three-dimensional model of the crankshaft according to the crankshaft system firing order and the structural size index.

[0077] It is worth mentioning that each module involved in the embodiment is a logical module. In actual application, one logical unit can be one physical unit, or a part of one physical unit, or realized by a combination of multiple physical units. In addition, in order to highlight the innovative part of the present application, the units not closely related to solving the technical problems proposed in the present application are not introduced in the embodiment, but this does not mean that there are no other units in the embodiment.

[0078] It should be noted that in the present disclosure, the terms "comprise", "contain" or any other variants thereof are intended to cover non-exclusive inclusion, so that the process, method, article or equipment including a series of elements not only includes those elements, but also includes other elements not explicitly listed or inherent to such process, method, article or equipment. Without more limitations, the element limited by the statement "including a" does not exclude the presence of another identical element in the process, method, article or equipment including the element.

[0079] Embodiment five: Another embodiment of the present application relates to an electronic device, such as Figure 6 as shown, comprising: at least one processor; and a memory connected in communication with the at least one processor; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to perform the steps of the following method: obtaining a three-dimensional model of a crankshaft satisfying preset crankshaft design requirements, the preset crankshaft design requirements including structural parameters of pistons, connecting rod necks and cylinders, and performance characteristic parameters of the whole machine; determining balance weight rearrangement combinations based on the three-dimensional model of the crankshaft, the balance weight rearrangement combinations including structures, quantities and arrangement positions of balance weights; calculating balance rates of each of the balance weight rearrangement combinations, and screening a candidate balance weight rearrangement combination from each of the balance weight rearrangement combinations according to the balance rates; detecting whether characteristic parameters of a crankshaft arranged with the candidate balance weight rearrangement combination satisfy preset index requirements; determining that the candidate balance weight rearrangement combination corresponding to the crankshaft whose characteristic parameters satisfy the preset index requirements is an optimal balance weight rearrangement combination.

[0080] In one embodiment, the processor, when executing the computer program, further implements the following steps: calculating a first resultant unbalanced torque when there is no balance weight based on the three-dimensional model of the crankshaft, and a second resultant unbalanced torque under each of the balance weight rearrangement combinations; determining the balance rates of each of the balance weight rearrangement combinations based on the first resultant unbalanced torque and the second resultant unbalanced torque; screening a candidate balance weight rearrangement combination from each of the balance weight rearrangement combinations according to the balance rates.

[0081] In one embodiment, the processor, when executing the computer program, further implements the following steps: obtaining an unbalanced torque in a horizontal direction of a shafting of the crankshaft and an unbalanced torque in a vertical direction of the shafting when there is no balance weight; determining the first resultant unbalanced torque based on the unbalanced torque in the horizontal direction of the shafting of the crankshaft and the unbalanced torque in the vertical direction of the shafting when there is no balance weight; obtaining the unbalanced torque in the horizontal direction of the shafting of the crankshaft and the unbalanced torque in the vertical direction of the shafting under each of the balance weight rearrangement combinations; determining the second resultant unbalanced torque based on the unbalanced torque in the horizontal direction of the shafting of the crankshaft and the unbalanced torque in the vertical direction of the shafting under each of the balance weight rearrangement combinations.

[0082] In one embodiment, an expression of the unbalanced torque in the horizontal direction of the shafting is: = maRw2[ sin(Φ ) + sin(Φ ) +... + sin(Φ ) ] ; The expression of the shaft system vertical direction unbalance moment is: = maRw2[ cos(Φ ) + cos(Φ ) +... + cos(Φ ) ]. The expression of the shaft system combined unbalance moment is: ΣM=

[0083] wherein, is the axial horizontal direction unbalance moment, is the axial horizontal direction unbalance moment, ΣM is the axial horizontal direction unbalance moment, Φ is the included angle between the first crank and the vertical center line, Z is the cylinder number (crank number), , ... is the included angle between each crank and the first crank, , ... is the distance between each cylinder (connecting rod neck) center line and the crankshaft center shaft neck vertical center line.

[0084] In one embodiment, the expression of the balance rate is: P=

[0085] wherein, P is the balance rate, is the first combined unbalance moment calculated when the shaft system has no balance weight, is the second combined unbalance moment calculated when the shaft system has different balance weight arrangement schemes.

[0086] In one embodiment, the characteristic parameters include torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency, and oil film thickness.

[0087] In one embodiment, the processor further implements the following steps when executing the computer program: acquiring preset crankshaft design requirements, the preset crankshaft design requirements including structural parameters of pistons, connecting rod necks, and cylinders, and whole machine performance characteristic parameters; determining a crankshaft system firing order and structural size index according to the preset crankshaft design requirements; constructing a crankshaft three-dimensional model according to the crankshaft system firing order and structural size index.

[0088] The memory and the processor are connected by a bus, which can include any number of interconnecting buses and bridges, and the bus connects the various circuits of the one or more processors and the memory together. The bus can also connect various other circuits such as peripheral devices, voltage regulators, and power management circuits, which are well known in the art, and therefore, will not be described any further. A bus interface provides an interface between the bus and a transceiver. The transceiver, which can be a single element or a plurality of elements, such as a plurality of receivers and transmitters, provides a communication path for communicating with various other devices over a transmission medium. Data processed by the processor is transmitted over a wireless medium via an antenna, and further, the antenna also receives data and delivers the data to the processor.

[0089] The processor is responsible for managing the bus and general processing, and can also provide various functions including timing, peripheral interfaces, voltage regulation, power management, and other control functions. The memory can be used for storing data used by the processor while executing operations.

[0090] The processor can include, but is not limited to, one or more processors or microprocessors, etc. Each processor can be an Application Specific Integrated Circuit (ASIC), a Digital Signal Processor (DSP), a Digital Signal Processing Device (DSPD), a Programmable Logic Device (PLD), a Field Programmable Gate Array (FPGA), a controller, a microcontroller, a microprocessor, or other electronic elements implemented to perform the methods in the above embodiments.

[0091] Embodiment six: Another embodiment of the present application relates to a computer readable storage medium storing a computer program. The computer program is executed by a processor to implement the steps of the following method: Obtaining a crankshaft three-dimensional model satisfying preset crankshaft design requirements, the preset crankshaft design requirements including structural parameters of a piston, a connecting rod neck, and a cylinder, and whole machine performance characteristic parameters; Determining a balance weight rearrangement combination based on the crankshaft three-dimensional model, the balance weight rearrangement combination including a balance weight structure, a balance weight number, and a rearrangement position; Calculating balance rates of each balance weight rearrangement combination, and screening a candidate balance weight rearrangement combination from each balance weight rearrangement combination according to the balance rates; determine whether the characteristic parameter of the crankshaft arranged with the candidate balance weight rearrangement combination meets preset index requirements; determine that the candidate balance weight rearrangement combination corresponding to the crankshaft whose characteristic parameter meets preset index requirements is a preferred balance weight rearrangement combination.

[0092] In one embodiment, the computer program, when executed by the processor, further implements the following steps: based on the three-dimensional model of the crankshaft, calculate a first resultant unbalanced torque when there is no balance weight, and a second resultant unbalanced torque under each of the balance weight rearrangement combinations; determine the balance rate of each of the balance weight rearrangement combinations based on the first resultant unbalanced torque and the second resultant unbalanced torque; select a candidate balance weight rearrangement combination from each of the balance weight rearrangement combinations according to the balance rate.

[0093] In one embodiment, the computer program, when executed by the processor, further implements the following steps: obtain the shafting horizontal direction unbalanced torque and the shafting vertical direction unbalanced torque of the crankshaft when there is no balance weight; determine the first resultant unbalanced torque based on the shafting horizontal direction unbalanced torque and the shafting vertical direction unbalanced torque of the crankshaft when there is no balance weight; obtain the shafting horizontal direction unbalanced torque and the shafting vertical direction unbalanced torque of the crankshaft under each of the balance weight rearrangement combinations; determine the second resultant unbalanced torque based on the shafting horizontal direction unbalanced torque and the shafting vertical direction unbalanced torque of the crankshaft under each of the balance weight rearrangement combinations.

[0094] In one embodiment, the expression of the shafting horizontal direction unbalanced torque is: = maRw2[ sin(Φ+ ) + sin(Φ+ ) +... + sin(Φ+ ) ] ; The expression of the shafting vertical direction unbalanced torque is: = maRw2[ cos(Φ+ ) + cos(Φ+ ) +... + cos(Φ+ ) ] ; The expression of the shafting resultant unbalanced torque is: ∑M = ∑M

[0095] wherein, is the axial horizontal direction unbalance moment, is the axial horizontal direction unbalance moment, ∑M is the axial horizontal direction unbalance moment, Φ is the angle between the first crank and the vertical center line, Z is the number of cylinders (crank number), , ... is the angle between each crank and the first crank, , ... is the distance between each cylinder (connecting rod neck) center line and the crankshaft center axis neck vertical center line.

[0096] In one embodiment, the expression of the balance rate is: P = ∑M

[0097] wherein, P is the balance rate, is the first synthesized unbalance moment calculated when the shafting has no balance weight, is the second synthesized unbalance moment calculated when the shafting has different balance weight arrangement schemes.

[0098] In one embodiment, the characteristic parameters include torsional vibration amplitude, bearing lubrication, torsional vibration stress, natural frequency, and oil film thickness.

[0099] In one embodiment, the computer program, when executed by the processor, further implements the following steps: obtaining preset crankshaft design requirements, the preset crankshaft design requirements including structural parameters of pistons, connecting rod necks, and cylinders, and whole machine performance characteristic parameters; determining a crankshaft system firing order and a structure size index according to the preset crankshaft design requirements; constructing a crankshaft three-dimensional model according to the crankshaft system firing order and the structure size index.

[0100] That is, those skilled in the art can understand that all or part of the steps in the above-mentioned embodiment methods can be completed by a program instructing related hardware, the program being stored in a storage medium and including a plurality of instructions for causing a device (which can be a single-chip microcomputer, a chip, etc.) or a processor to execute all or part of the steps of the method described in each embodiment of the present application. The foregoing storage medium includes a U disk, a mobile hard disk, a read-only memory (ROM), a random access memory (RAM), a magnetic disk or an optical disk, and various media that can store program codes.

[0101] The computer-readable storage medium can also store at least one computer executable program / instruction, for example, computer-readable instructions. The computer-readable storage medium includes, but is not limited to, for example, volatile memory and / or non-volatile memory. The volatile memory can include, for example, random access memory (RAM), cache memory, and / or the like. The computer-readable storage medium can include, for example, read-only memory (ROM), a hard disk, a flash memory, and / or the like. For example, the non-transitory computer-readable storage medium can be connected to a computing device such as a computer, and then, in a case where the computing device executes the computer-readable instructions stored on the computer-readable storage medium, each method as described above can be performed.

[0102] In addition, the computer device can further include, but is not limited to, a data bus, an input / output (I / O) bus, a display, and an input / output device (for example, a keyboard, a mouse, a speaker, and / or the like), and / or the like.

[0103] The processor can communicate with an external device via a wired or wireless network through the I / O bus.

[0104] It will be understood by those of ordinary skill in the art that the above-described embodiments are specific embodiments for implementing the present application, and various changes can be made in form and details in actual application without departing from the spirit and scope of the present application.

Claims

1. A method of designing a crankshaft for an electrical generator, the method comprising: The method comprises the following steps: obtaining a three-dimensional model of a crankshaft satisfying preset crankshaft design requirements, wherein the preset crankshaft design requirements comprise structural parameters of pistons, connecting rod necks and cylinders, and performance characteristic parameters of the whole machine; determining a balance weight rearrangement combination based on the three-dimensional model of the crankshaft, wherein the balance weight rearrangement combination comprises the structure, quantity and arrangement position of balance weights; calculating balance rates of each balance weight rearrangement combination, and screening a candidate balance weight rearrangement combination from each balance weight rearrangement combination according to the balance rates; detecting whether characteristic parameters of a crankshaft arranged with the candidate balance weight rearrangement combination satisfy preset index requirements; determining that the candidate balance weight rearrangement combination corresponding to the crankshaft whose characteristic parameters satisfy the preset index requirements is an optimal balance weight rearrangement combination.

2. The method of designing a generator crankshaft according to claim 1, wherein, The step of calculating balance rates of each balance weight rearrangement combination and screening a candidate balance weight rearrangement combination from each balance weight rearrangement combination according to the balance rates comprises the following steps: calculating a first synthesized unbalanced torque when there is no balance weight based on the three-dimensional model of the crankshaft, and calculating a second synthesized unbalanced torque under each balance weight rearrangement combination; determining the balance rates of each balance weight rearrangement combination based on the first synthesized unbalanced torque and the second synthesized unbalanced torque; screening a candidate balance weight rearrangement combination from each balance weight rearrangement combination according to the balance rates.

3. The method of claim 2, wherein, The step of calculating a first synthesized unbalanced torque when there is no balance weight based on the three-dimensional model of the crankshaft, and calculating a second synthesized unbalanced torque under each balance weight rearrangement combination comprises the following steps: obtaining an unbalanced torque in a horizontal direction of a shafting of the crankshaft and an unbalanced torque in a vertical direction of the shafting when there is no balance weight; determining the first synthesized unbalanced torque based on the unbalanced torque in the horizontal direction of the shafting of the crankshaft and the unbalanced torque in the vertical direction of the shafting when there is no balance weight; obtaining an unbalanced torque in a horizontal direction of a shafting of the crankshaft and an unbalanced torque in a vertical direction of the shafting under each balance weight rearrangement combination; determining the second synthesized unbalanced torque based on the unbalanced torque in the horizontal direction of the shafting of the crankshaft and the unbalanced torque in the vertical direction of the shafting under each balance weight rearrangement combination.

4. The method of designing a generator crankshaft according to claim 3, wherein, The expression of the unbalanced torque in the horizontal direction of the shafting is: = maRw2[ sin(Φ ) + sin(Φ ) +... + sin(Φ ) ] ; The expression of the unbalanced torque in the vertical direction of the shafting is: = maRw2[ cos(Φ ) + cos(Φ ) +... + cos(Φ ) ] ; The expression of the synthesized unbalanced torque of the shafting is: ∑M = 0 wherein, is the axial horizontal direction unbalance moment, is the axial horizontal direction unbalance moment, ΣM is the axial horizontal direction unbalance moment, Φ is the included angle between the 1st crank and the vertical center line, and Z is the number of cylinders (number of cranks), , ... is the included angle between each crank and the 1st crank, , ... is the distance between each cylinder (big end of connecting rod) center line and the vertical center line of the crankshaft center journal.

5. The method of claim 2, wherein, The expression of the balance rate is: P= Wherein, P is the balance rate, is the first synthetic unbalance moment calculated when the shafting is without counterweight, is the second synthetic unbalance moment calculated when the shafting is under different counterweight arrangement schemes.

6. The method of designing a generator crankshaft of claim 1, wherein, The characteristic parameters comprise torsional vibration amplitudes, bearing lubrication, torsional vibration stresses, natural frequencies and oil film thicknesses.

7. The method of claim 1, wherein, The step of obtaining a three-dimensional model of a crankshaft satisfying preset crankshaft design requirements, wherein the preset crankshaft design requirements comprise structural parameters of pistons, connecting rod necks and cylinders, and performance characteristic parameters of the whole machine comprises the following steps: obtaining preset crankshaft design requirements, wherein the preset crankshaft design requirements comprise structural parameters of pistons, connecting rod necks and cylinders, and performance characteristic parameters of the whole machine; determining a crankshaft firing sequence and structural size index according to the preset crankshaft design requirements; constructing a three-dimensional model of the crankshaft according to the crankshaft firing sequence and the structural size index.

8. An electric generator crankshaft design apparatus characterized by comprising: The method comprises the following steps: An acquisition module is configured to acquire a three-dimensional model of a crankshaft that meets preset crankshaft design requirements, the preset crankshaft design requirements including structural parameters of pistons, connecting rod necks, and cylinders, and whole-machine performance characteristic parameters; An arrangement combination determination module is configured to determine a balance weight arrangement combination based on the three-dimensional model of the crankshaft, the balance weight arrangement combination including structures, quantities, and arrangement positions of balance weights; A balance rate calculation module is configured to calculate balance rates of each balance weight arrangement combination, and to screen a candidate balance weight arrangement combination from each balance weight arrangement combination according to the balance rates; A detection module is configured to detect whether characteristic parameters of a crankshaft arranged with the candidate balance weight arrangement combination meet preset index requirements; A preferred module is configured to determine that the candidate balance weight arrangement combination corresponding to the crankshaft whose characteristic parameters meet the preset index requirements is a preferred balance weight arrangement combination.

9. An electronic device, comprising: comprise: at least one processor; and a memory connected with the at least one processor in communication; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to perform the generator crankshaft design method according to any one of claims 1 to 7.

10. A computer readable storage medium storing a computer program, characterized in that, The computer program is executed by the processor to implement the generator crankshaft design method according to any one of claims 1 to 7.

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