CN114033692B

CN114033692B - Balance block group and design method and device thereof, storage medium and processor

Info

Publication number: CN114033692B
Application number: CN202111396039.6A
Authority: CN
Inventors: 黄创; 谷欢欢; 张荣婷; 张金圈; 杨彬; 孙万杰
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-11-23
Filing date: 2021-11-23
Publication date: 2023-03-21
Anticipated expiration: 2041-11-23
Also published as: CN114033692A

Abstract

The invention discloses a method and a device for designing a balance block group, the balance block group, a storage medium and a processor, wherein the method comprises the following steps: designing basic parameters of a balancing block group based on a force balance relation and a moment balance relation at a first set speed; determining the shaft system deflection caused by the centrifugal force of a dynamic disc eccentric part and a balance block group of the scroll compressor; designing a configuration of a balancing block group capable of adjusting the eccentricity according to a dynamic disc eccentric part of the scroll compressor and shafting deflection caused by the centrifugal force of the balancing block group; designing structural parameters of a balancing block group capable of adjusting the eccentricity amount based on the force balance relationship and the moment balance relationship at a second set speed in combination with the basic parameters; the second set speed is greater than the first set speed. According to the scheme, the balance block of shafting deflection is considered through design, the balance block is utilized to restrain the crankshaft from generating deflection when the scroll compressor is at a high speed, and the working performance of the scroll compressor is ensured.

Description

Balance block group and design method and device thereof, storage medium and processor

Technical Field

The invention belongs to the technical field of compressors, and particularly relates to a balance block group design method, a balance block group design device, a balance block group, a storage medium and a processor, in particular to a balance block design method, a balance block group design device, a balance block group design medium and a processor considering shafting deflection.

Background

The eccentric part of the scroll compressor crankshaft brings unbalanced force and unbalanced moment to the shafting; a main balance block and an auxiliary balance block are required to be designed to balance unbalanced force and unbalanced moment. Along with the high speed of the scroll compressor, the excessive centrifugal force of the eccentric part, the main balance block and the auxiliary balance block of the scroll compressor crankshaft can cause the deflection of the scroll compressor crankshaft, the lubrication of the bearing is poor, and the bearing endurance is reduced; meanwhile, additional unbalanced force and unbalanced moment are brought to a shafting, and the problem of large 1-frequency-doubling vibration noise is caused.

The above is only for the purpose of assisting understanding of the technical aspects of the present invention, and does not represent an admission that the above is prior art.

Disclosure of Invention

The invention aims to provide a design method and a device of a balance block group, the balance block group, a storage medium and a processor, which are used for solving the problems that the bearing endurance is reduced due to the deflection of a crankshaft when a scroll compressor is at a high speed, a shaft system generates larger vibration noise and the working performance of the scroll compressor is influenced, and achieving the effect of ensuring the working performance of the scroll compressor by designing a balance block considering the deflection of the shaft system, inhibiting the deflection of the crankshaft by using the balance block when the scroll compressor is at the high speed, avoiding the reduction of the bearing endurance and the larger vibration noise of the shaft system due to the deflection of the crankshaft.

The invention provides a design method of a balance block group, wherein the balance block group can be applied to a scroll compressor; the balancing block group comprises: a primary balance weight and a secondary balance weight; the design method of the balancing block group comprises the following steps: designing basic parameters of the balancing block group based on a force balance relation and a moment balance relation at a first set speed; determining the shaft system deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group of the scroll compressor; designing a configuration of the balance block group capable of adjusting the eccentricity according to a dynamic disc eccentric part of the scroll compressor and shafting deflection caused by the centrifugal force of the balance block group; the eccentricity amount comprises: a second eccentricity of the balancing block set; designing structural parameters of the balancing block group capable of adjusting the eccentricity based on the force balance relationship and the moment balance relationship at a second set speed in combination with the basic parameters; the second set speed is greater than the first set speed.

In some embodiments, designing the basic parameters of the balancing mass set based on the force balance relationship and the moment balance relationship at the first set speed comprises: determining a force balance relationship and a moment balance relationship at a first set speed according to equation (1):

wherein m is _p 、e _p Mass and eccentricity of the main balance weight, m _a 、e _a Mass and eccentricity of the auxiliary balance weight, m _e 、e _e Respectively the mass and the eccentricity of the eccentric portion, L _p 、L _a The distances from the mass center of the main balance block and the mass center of the auxiliary balance block to the mass center of the eccentric part are respectively; and determining the mass and the eccentric amount of the main balancing block and the mass and the eccentric amount of the auxiliary balancing block as the basic parameters of the balancing block set by combining the structural parameters of the basic configuration of the balancing block set and the force balance relationship and the moment balance relationship at the first set speed.

In some embodiments, determining the shafting deflection caused by the centrifugal force of the set of balance blocks and the dynamic disk eccentric of the scroll compressor comprises: according to a formula (2), coupling iterative shafting deflection and bearing rigidity under the deflection, and calculating shafting deflection caused by centrifugal force of the dynamic disc eccentric part and the balance block group through iterative convergence:

u _{dis_i+1} ＝u _{dis_i} +alpha*((K _shaft +K _bearing ) ^-1 F _external -u _{dis_i} ) (2)；

wherein u is _{dis_i} 、u _{dis_i+1} The axis deflection of the iteration step and the next iteration step, alpha is an iteration relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector; the centrifugal force of the balancing block set comprises: the centrifugal force of the primary weight, and the centrifugal force of the secondary weight.

In some embodiments, coupling iterative shafting deflection and bearing stiffness at the deflection to each other, and iteratively converging to calculate shafting deflection caused by centrifugal force of the dynamic disk eccentric portion and the balance block group, comprises: inputting structural parameters, material parameters and external load of a shaft of the scroll compressor, the position and the structural parameters of a bearing of the scroll compressor, and calculating the allowable maximum iteration step number, the calculation precision and the initial value of the deflection of the shaft system; establishing a finite element model of a shaft of the scroll compressor to obtain an overall stiffness matrix of the shaft; obtaining a load vector according to the finite element model of the shaft and the external load; calculating to obtain an initial value of the rigidity of the sliding bearing of the scroll compressor based on the initial value of the deflection; coupling the integral rigidity array of the shaft and the initial value of the rigidity of the sliding bearing to form a system rigidity array; processing the system stiffness array and the load vector before nonlinear iteration to obtain the deflection of the shaft; and within the allowed maximum iteration step number, if the deflection of the shaft reaches the calculation precision, outputting the deflection of the shaft, the rigidity of each bearing and the damping iteration times to determine the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group.

In some embodiments, designing the configuration of the balance block set capable of adjusting the eccentricity amount according to the dynamic disc eccentric portion of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set comprises: designing the configuration of the main balance weight; wherein the configuration of the main balance weight comprises: the main balance weight assembly comprises a main balance weight main body, a main balance weight cover plate arranged on the main balance weight main body, and a main balance weight mass component arranged in the main balance weight cover plate; designing the configuration of the secondary balance weight; wherein the configuration of the secondary weight comprises: the auxiliary balance weight assembly comprises an auxiliary balance weight main body, an auxiliary balance weight cover plate arranged on the auxiliary balance weight main body, and an auxiliary balance weight mass component arranged in the auxiliary balance weight cover plate; the main balance weight mass component and the auxiliary balance weight mass component can adjust the eccentric amount.

In some embodiments, a main balance weight mounting groove and a first guide rail are provided in the main balance weight cover plate; the first guide rail is arranged in a hole formed between the main balance weight cover plate and the main balance weight; the main balance weight mass assembly can move along the first guide rail; the primary counterbalance mass assembly comprising: a first wave spring, a first movable mass and a first damping layer; the first movable mass disposed between the first wave spring and the first damping layer; the secondary counterbalancing mass assembly comprising: the auxiliary balance block cover plate is provided with an auxiliary balance block mounting groove and a second guide rail; the second guide rail is arranged in a hole formed between the auxiliary balance block cover plate and the auxiliary balance block; the auxiliary balance weight mass component can move along the second guide rail; the secondary counterbalancing mass assembly comprising: a second wave spring, a second movable mass and a second damping layer; the second movable mass disposed between the second wave spring and the second damping layer.

In some embodiments, designing the structural parameters of the balancing block set capable of adjusting the eccentricity amount based on the force balance relationship and the moment balance relationship at the second set speed in combination with the basic parameters comprises: and (3) determining the force balance relation and the moment balance relation at the second set speed according to the formula (3):

wherein L is _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the rotor of the machine, delta _p Deflection at the position of the center of mass of the main balance weight, delta _a Is the deflection of the position of the mass center of the auxiliary balance block delta _m The deflection is the position of the center of mass of the motor rotor; and determining the structural parameters of the balancing block group capable of adjusting the eccentricity according to the basic parameters and the formula (3).

In another aspect, the invention provides a device for designing a balancing block set, wherein the balancing block set can be applied to a scroll compressor; the balancing block group comprises: a primary balance weight and a secondary balance weight; the design device of the balancing block group comprises: a design unit configured to design basic parameters of the balance block group based on a force balance relationship and a moment balance relationship at a first set speed; the design unit is further configured to determine a dynamic disc eccentric portion of the scroll compressor and a shafting deflection caused by a centrifugal force of the balance block group; the design unit is further configured to design the configuration of the balance block group capable of adjusting the eccentricity amount according to the dynamic disc eccentric part of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block group; the eccentricity amount comprises: a second eccentricity of the balancing block set; the design unit is further configured to design a structural parameter of the balancing block group capable of adjusting the eccentricity amount based on a force balance relation and a moment balance relation at a second set speed in combination with the basic parameter; the second set speed is greater than the first set speed.

In some embodiments, the designing unit, based on the force balance relationship and the moment balance relationship at the first set speed, designs the basic parameters of the balancing block set, including: according to the formula (1), determining the force balance relation and the moment balance relation at the first set speed:

wherein m is _p 、e _p Mass and eccentricity of the main balance weight, m _a 、e _a Mass and eccentricity of the auxiliary balance weight, m _e 、e _e Respectively mass and eccentricity of the eccentric portion, L _p 、L _a The distances from the mass center of the main balance block and the mass center of the auxiliary balance block to the mass center of the eccentric part are respectively; and determining the mass and the eccentric amount of the main balancing block and the mass and the eccentric amount of the auxiliary balancing block as the basic parameters of the balancing block set by combining the structural parameters of the basic configuration of the balancing block set and the force balance relationship and the moment balance relationship at the first set speed.

In some embodiments, the design unit, determining a dynamic disc eccentric of the scroll compressor and a shafting deflection caused by a centrifugal force of the balance block set, comprises: according to a formula (2), coupling iterative shafting deflection and bearing rigidity under the deflection, and calculating shafting deflection caused by centrifugal force of the dynamic disc eccentric part and the balance block group through iterative convergence:

In some embodiments, the designing unit, which couples the iterative shafting deflection and the bearing stiffness under the deflection to each other, and iteratively converges and calculates the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group, includes: inputting structural parameters, material parameters and external load of a shaft of the scroll compressor, the position and structural parameters of a bearing of the scroll compressor, and calculating the maximum allowable iteration step number, calculation precision and initial value of deflection of the shaft system deflection; establishing a finite element model of a shaft of the scroll compressor to obtain an integral rigidity matrix of the shaft; obtaining a load vector according to the finite element model of the shaft and the external load; calculating to obtain an initial value of the rigidity of the sliding bearing of the scroll compressor based on the initial value of the deflection; coupling the integral rigidity array of the shaft and the initial value of the rigidity of the sliding bearing to form a system rigidity array; processing the system stiffness array and the load vector before nonlinear iteration to obtain the deflection of the shaft; and within the allowed maximum iteration step number, if the deflection of the shaft reaches the calculation precision, outputting the deflection of the shaft, the rigidity of each bearing and the damping iteration times to determine the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group.

In some embodiments, the designing unit, based on the dynamic disc eccentric portion of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set, designs the configuration of the balance block set capable of adjusting the eccentric amount, including: designing the configuration of the main balance weight; wherein the configuration of the main balance weight comprises: the main balance weight assembly comprises a main balance weight main body, a main balance weight cover plate arranged on the main balance weight main body, and a main balance weight mass component arranged in the main balance weight cover plate; designing the configuration of the secondary balance weight; wherein the configuration of the secondary weight comprises: the auxiliary balance weight assembly comprises an auxiliary balance weight main body, an auxiliary balance weight cover plate arranged on the auxiliary balance weight main body, and an auxiliary balance weight mass component arranged in the auxiliary balance weight cover plate; the main balance weight mass component and the auxiliary balance weight mass component can adjust the eccentric amount.

In some embodiments, a main balance weight mounting groove and a first guide rail are provided in the main balance weight cover plate; the first guide rail is arranged in a hole formed between the main balance weight cover plate and the main balance weight; the main balance weight mass assembly can move along the first guide rail; the primary counterbalance mass assembly comprising: a first wave spring, a first movable mass and a first damping layer; the first movable mass disposed between the first wave spring and the first damping layer; the secondary counterbalancing mass assembly comprising: the auxiliary balance block cover plate is provided with an auxiliary balance block mounting groove and a second guide rail; the second guide rail is arranged in a hole formed between the auxiliary balance block cover plate and the auxiliary balance block; the auxiliary balance weight mass component can move along the second guide rail; the secondary counterbalancing mass assembly comprising: a second wave spring, a second movable mass and a second damping layer; the second movable mass is disposed between the second wave spring and the second damping layer.

In some embodiments, the designing unit, based on the force balance relationship and the moment balance relationship at the second set speed, and in combination with the basic parameters, designs the structural parameters of the balancing block set capable of adjusting the eccentricity, including: and (3) determining the force balance relation and the moment balance relation at the second set speed according to the formula (3):

wherein L is _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the rotor of the machine, delta _p Is the position of the mass center of the main balance blockDeflection, delta _a Is the deflection of the center of mass position of the auxiliary balance block delta _m The deflection is the position of the center of mass of the motor rotor; and determining the structural parameters of the balancing block group capable of adjusting the eccentricity according to the basic parameters and the formula (3).

In accordance with the above device, a further aspect of the present invention provides a balancing block set, which is obtained by the above method for designing a balancing block set, or by the above device for designing a balancing block set.

In accordance with the foregoing method, a further aspect of the present invention provides a storage medium, where the storage medium includes a stored program, and when the program runs, the apparatus on which the storage medium is located is controlled to execute the above method for designing a balancing block group.

In accordance with the method, a further aspect of the present invention provides a processor for running a program, wherein the program executes the method for designing a balancing block group as described above.

Therefore, in the scheme of the invention, the balance block group with the adjustable eccentricity is designed under the condition of considering the shafting deflection, and the balance block group with the adjustable eccentricity is utilized to realize the great inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring the low-speed balance; therefore, by designing the balance block considering the deflection of the shaft system, the balance block is utilized to inhibit the deflection of the crankshaft when the scroll compressor is at a high speed, the bearing endurance is prevented from being reduced and the shaft system is prevented from generating larger vibration noise due to the deflection of the crankshaft, and the working performance of the scroll compressor is ensured.

Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

The technical solution of the present invention is further described in detail by the accompanying drawings and embodiments.

Drawings

FIG. 1 is a flowchart illustrating an embodiment of a method for designing a balancing block set according to the present invention;

FIG. 2 is a schematic flow chart illustrating an embodiment of basic parameters for designing the balancing block set in the method of the present invention;

FIG. 3 is a schematic flow chart of an embodiment of calculating the shafting deflection caused by the centrifugal force of the movable disk eccentric part and the balancing block group by iterative convergence in the method of the present invention;

FIG. 4 is a schematic flowchart of an embodiment of designing a structural parameter of the balancing block set capable of adjusting the eccentricity amount in the method of the present invention;

FIG. 5 is a schematic structural diagram of an embodiment of a device for designing a balancing block set according to the present invention;

FIG. 6 is a schematic flow chart illustrating an embodiment of a deflection balancing weight design method according to the present invention;

FIG. 7 is a schematic flow chart illustrating an embodiment of a method for calculating shafting deflection in the method for designing a balance weight considering deflection according to the present invention;

FIG. 8 is a schematic view of the shafting assembly structure with the main balance weight and the auxiliary balance weight according to the present invention;

FIG. 9 is a schematic front view of a main weight of the present invention;

FIG. 10 isbase:Sub>A right side cross-sectional view of the primary weight of the present invention, particularly the cross-sectional view along the line A-A of FIG. 9;

FIG. 11 is a schematic three-dimensional structure of a primary weight of the present invention;

FIG. 12 is a schematic front view of a secondary weight of the present invention;

FIG. 13 is a right side cross-sectional view of the secondary weight of the present invention, particularly the cross-sectional view along the line B-B of FIG. 12;

FIG. 14 is a schematic three-dimensional structure of a secondary balance weight according to the present invention.

The reference numbers in the embodiments of the present invention are as follows, in combination with the accompanying drawings:

1-an eccentric portion; 2-a main balance block with adjustable eccentricity; 21-a first wave spring (i.e. the wave spring of the primary weight); 22-a first movable mass (i.e. the movable mass of the primary counterweight); 23-a first damping layer glued to the first movable mass (i.e. the first damping layer of the primary weight); 24-a main counterweight cover plate; 25 — first guide rail (i.e. guide rail of the main counterweight); 26-a main counterweight body; 27 — first screw hole (i.e., screw hole of primary weight); 3-auxiliary balance block with adjustable eccentricity; 31-a second wave spring (i.e. the wave spring of the secondary weight); 32-a second movable mass (i.e. the movable mass of the secondary balance mass); 33-a second damping layer (i.e. of the secondary balance mass) glued to the second movable mass; 34-an auxiliary balance block cover plate; 35-second rail (i.e. rail of secondary counterweight); 36-a secondary counterbalance body; 37-a second screw hole (i.e., the screw hole of the secondary weight); 4-motor rotor.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the specific embodiments of the present invention and the accompanying drawings. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, belong to the protection scope of the present invention.

Among the related schemes, schemes for suppressing the deflection of the shafting caused by the centrifugal force are few. On one hand, the centrifugal force is changed along with the rotating speed, the deflection required to be balanced at low speed is small, the deflection required to be balanced at high speed is large, and the two are difficult to be considered at the same time. On the other hand, the axial structure of the scroll compressor shaft system is compact, the space of the implementation scheme can be allowed to be smaller, and the layout and the structure of the shaft system and the bracket are generally required to be greatly changed.

Some proposals have been made for a balance weight with an adjustable eccentricity to balance the centrifugal force of the orbiting scroll over a range of low to high speeds. However, the scheme has the problems that the movable mass block cannot be assembled, the problem that the shafting generates deflection due to centrifugal force is not involved, and the structures of the corresponding main balance block and the auxiliary balance block are not involved.

In other schemes, an additional balancing block group is required to be added to offset shafting deflection caused by centrifugal force of the eccentric part, the main balancing block and the auxiliary balancing block, and the scheme can inhibit the shafting deflection caused by the centrifugal force in a range from low speed to high speed but is limited by the axial space of the shafting, particularly the position of the eccentric part.

Still some schemes expand the inside cavity of scroll compressor upper bracket to including main balancing piece wherein, through shortening the effect distance of main balancing piece centrifugal force, realized that shafting amount of deflection reduces by a wide margin, nevertheless this scheme will lead to main bearing rigidity to reduce and increase the upper bracket and make the degree of difficulty.

According to an embodiment of the present invention, a method for designing a balancing block group is provided, as shown in fig. 1, which is a schematic flow chart of an embodiment of the method of the present invention. The balance block group can be applied to the scroll compressor. The balancing block group comprises: a primary weight and a secondary weight. The design method of the balancing block group comprises the following steps: step S110 to step S140.

At step S110, basic parameters of the balancing block set are designed based on the force balance relationship and the moment balance relationship at the first set speed. A first set speed, such as a low speed.

In some embodiments, the specific process of designing the basic parameters of the balancing block set based on the force balance relationship and the moment balance relationship at the first set speed in step S110 is as follows.

The following further describes a specific process of designing the basic parameters of the balancing block set in step S120, with reference to a flowchart of an embodiment of designing the basic parameters of the balancing block set in the method of the present invention shown in fig. 2, including: step S210 and step S220.

Step S210, according to the formula (1), determining a force balance relation and a moment balance relation under a first set speed:

wherein m is _p 、e _p Mass and eccentricity of the main balance weight, m _a 、e _a Mass and eccentricity of the auxiliary balance weight, m _e 、e _e Respectively the mass and the eccentricity of the eccentric portion, L _p 、L _a The distances from the mass center of the main balance block and the mass center of the auxiliary balance block to the mass center of the eccentric part are respectively.

Step S220, determining the mass and the eccentric amount of the main balancing block and the mass and the eccentric amount of the auxiliary balancing block as the basic parameters of the balancing block set, according to the structural parameters of the basic configuration of the balancing block set, and the force balance relationship and the moment balance relationship at the first set speed.

FIG. 6 is a flowchart illustrating an embodiment of a method for designing a weight considering deflection according to the present invention. The design flow of the design method of the balance block considering the deflection provided by the scheme of the invention is shown in figure 6, firstly, the mass and the eccentric amount of the main balance block and the auxiliary balance block are designed according to the force balance and the moment balance at the low speed, and then, the force balance and the moment balance at the low speed and the force balance and the moment balance considering the deflection at the high speed are simultaneously satisfied by adjusting the eccentric amount of the main balance block and the auxiliary balance block at the high speed. Specifically, as shown in fig. 6, the design method of the balance weight considering the deflection according to the solution of the present invention includes:

and 11, designing the mass, the eccentric amount and the structure of the main balance block and the negative balance block based on the force balance and the moment balance at low speed according to the mass and the eccentric amount of the eccentric part of the movable disc and the configuration (namely basic configuration) of the common balance block.

And step 12, under each excitation action, establishing a coupling model of the flexible shaft and the sliding bearing, and performing nonlinear iterative solution to obtain the deflection of the bearing, the deflection of the motor rotor and the deflection of the movable disc eccentric part.

And step 13, designing the configurations of the main balance block and the auxiliary balance block with adjustable eccentricity.

And step 14, satisfying low-speed balance and considering high balance of deflection, and iteratively designing structures of a main balance block and an auxiliary balance block with adjustable eccentricity.

In more detail, referring to the example shown in fig. 6, the design method of the balance weight considering deflection according to the solution of the present invention includes the following main steps:

the first step is as follows: the balance weight is designed based on force balance and moment balance at low speed.

The design method in the related scheme designs a balance block structure, and an equation which needs to satisfy force balance and moment balance at low speed is shown as a formula (1):

Based on the basic configuration (such as basic shape) of the main balance weight and the auxiliary balance weight, the mass m of the main balance weight can be measured _p Eccentricity e of the main balance weight _p Mass m of auxiliary balance block _a Eccentricity e of the auxiliary balance weight _a Is associated with the structural parameters, and m is obtained based on the optimization target such as minimum quality and the like on the premise of meeting the formula (1) _p 、e _p 、m _a 、e _a The value of (c). The structural parameters, such as the outer diameter and the inner diameter of the basic configuration of the main balance weight and the auxiliary balance weight, are the same.

Taking the structural parameters of the main balance weight as an example, as shown in fig. 9, after the basic configuration is determined, many parameters can be determined according to the assembly space and the process, and finally several main undetermined variables are determined, which are obtained by optimizing the balance weight mass minimum.

The parameters are determined according to the assembly space and the process, for example, as follows: as shown in fig. 9, the inner diameter of the mating hole with the crankshaft is determined by the outer diameter of the crankshaft, and the outer diameter of the mating hole is limited by the cold pressing process and the strength; the height of the base of the balance block is determined according to the highest point of the main bearing and the stator winding; the protruded fan ring selects the maximum value according to the inner diameter of the motor stator winding; the sector area, which contains the movable mass, is determined by the size of the movable mass, the springs and guides and the screw connections, preferably with a minimum height.

Formula (1) is to guarantee that the eccentric balancing block group of adjustable satisfies force and moment balance under the low-speed, and formula (1)'s the first formula is force balance, and the second formula is moment balance, can design the structural parameter and the initial value of movable mass piece and spring of the main balancing piece of basic configuration, vice balancing piece through formula (1).

At step S120, the dynamic disk eccentric portion of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set are determined.

In some embodiments, the determining of the shaft system deflection caused by the dynamic disk eccentricity of the scroll compressor and the centrifugal force of the balancing block set in step S120 comprises: according to a formula (2), coupling iterative shafting deflection with bearing rigidity under the deflection, and calculating shafting deflection caused by centrifugal force of the dynamic disc eccentric part and the balance block group through iterative convergence:

u _{dis_i+1} ＝u _{dis_i} +alpha*((K _shaft +K _bearing ) ^-1 F _external -u _{dis_i} ) (2)。

wherein u is _{dis_i} 、u _{dis_i+1} The axis deflection of the iteration step and the next iteration step, alpha is an iteration relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector. The centrifugal force of the balancing block set comprises: the centrifugal force of the main counterbalance, and the centrifugal force of the auxiliary counterbalance.

Referring to the example shown in fig. 6, the design method of the balance weight considering the deflection according to the present invention includes the following main steps:

the second step is that: and (5) calculating the shafting deflection under the action of centrifugal force.

The calculation flow of the shafting deflection under the action of the centrifugal force is shown in figure 7, the method couples the iterative shafting deflection and the bearing rigidity under the deflection, and iteratively converges to calculate the shafting deflection caused by the centrifugal force of the eccentric part of the dynamic disc, the main balance block and the auxiliary balance block, and the main iterative formula is as follows:

wherein u is _{dis_i} 、u _{dis_i+1} The axis deflection of the iteration step and the next iteration step, alpha is an iteration relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector.

If the iterative convergence meets the set error, the deflection delta at the position of the mass center of the main balance block can be obtained _p And the deflection delta of the center of mass position of the auxiliary balance block _a Deflection delta at the position of the center of mass of the motor rotor _m And deflection delta at the position of the center of mass of the eccentric part _e 。

The formula (2) is an iterative formula of shafting deflection calculation, because the compressor shafting contains the sliding bearing, the deflection is influenced by the rigidity and the damping of the sliding bearing, and simultaneously the rigidity and the damping of the sliding bearing are influenced by the deflection, if the shafting deflection under the action of external load needs to be solved, the axial deflection calculation can be realized by iterative calculation, and the specific flow is shown in fig. 7. The shafting deflection formed by assembling the structure calculated by the formula (1) under the centrifugal force load of the main balance block and the auxiliary balance block of the compressor can be calculated by the formula (2).

In some embodiments, iterative convergence calculates the specific process of shafting deflection caused by the centrifugal force of the rotor eccentric and the balance block group by coupling the iterative shafting deflection and the bearing stiffness under the deflection, see the following exemplary description.

The following further describes a specific process of calculating the shafting deflection caused by the centrifugal force of the dynamic disk eccentric portion and the balancing block group by iterative convergence, with reference to a schematic flow chart of an embodiment of calculating the shafting deflection caused by the centrifugal force of the dynamic disk eccentric portion and the balancing block group by iterative convergence in the method of the present invention shown in fig. 3, and the specific process includes: step S310 to step S340.

Step S310, inputting the structural parameters, the material parameters and the external load of the shaft of the scroll compressor, the position and the structural parameters of the bearing of the scroll compressor, and calculating the allowable maximum iteration step number, the calculation precision and the initial value of the deflection of the shaft system.

Step S320, establishing a finite element model of the shaft of the scroll compressor to obtain an overall stiffness matrix of the shaft. Obtaining a load vector according to the finite element model of the shaft and the external load; and calculating to obtain the initial value of the rigidity of the sliding bearing of the scroll compressor based on the initial value of the deflection.

And S330, coupling the integral rigidity array of the shaft and the initial value of the rigidity of the sliding bearing to form a system rigidity array. And processing the system stiffness array and the load vector before nonlinear iteration to obtain the deflection of the shaft.

And step S340, within the allowed maximum iteration step number, if the deflection of the shaft reaches the calculation precision, outputting the deflection of the shaft, the rigidity of each bearing and the damping iteration times to determine the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group.

Fig. 7 is a schematic flow chart of an embodiment of a method for calculating shafting deflection in the method for designing a balance weight considering deflection according to the present invention. Fig. 7 is a schematic flow chart of the shafting deflection calculation method in the second step in fig. 6. As shown in fig. 7, the method for calculating shafting deflection includes:

and step 21, inputting structural parameters, material parameters, external loads, bearing positions and structural parameters of the shaft, the maximum iteration step number allowed, calculation precision and an initial deflection value.

The structure parameters, material parameters, external load, bearing position and structure parameters of the input shaft are known quantities, and are obtained according to the design requirements, design flow and experience of the scroll compressor, and the patent only relates to the design of a balance block, so that the balance block can be directly used as the input quantity; the calculation precision can be set as the convergence precision of an iterative numerical algorithm; the deflection initial value is the displacement of a finite element node of a given shaft and can be calculated through the special condition of external load action and constant stiffness support.

And step 22, building a finite element model of the vertical shaft based on the Timoshenko beam unit to obtain an integral rigidity matrix of the shaft.

The Timoshenko beam is a beam capable of considering shear deformation, and displacement and section rotation angles of the Timoshenko beam are independently interpolated and are not obtained by a derivative of the displacement.

Step 23, obtaining a load vector according to the finite element model of the shaft and the external load;

and 24, calculating to obtain an initial value of the rigidity of the sliding bearing based on the initial value of the deflection.

And 25, coupling the integral rigidity array of the shaft and the rigidity of the bearing to form a system rigidity array.

And 26, preprocessing the system stiffness array and the load vector before nonlinear iteration. Because nonlinear iteration of variable bearing stiffness is needed, convergence is not easy by adopting a conventional Gaussian elimination method, an iteration numerical algorithm such as SSOR iteration needs to be adopted, a stiffness matrix needs to be divided into an upper triangle matrix, a diagonal matrix and a lower triangle matrix for iteration, and the SSOR iteration algorithm can be referred specifically.

And 27, solving to obtain the deflection of the shaft.

And step 28, judging whether the deflection meets the set precision: if yes, the deflection of the output shaft, the rigidity of each bearing and the damping iteration number. Otherwise, step 29 is performed.

Step 29, judging the number of iteration steps (i.e. whether the number of iterations exceeds a set value): if yes, ending the shafting deflection calculation process. Otherwise, calculating a new deflection value, calculating each bearing load, calculating each bearing stiffness according to a nonlinear iterative algorithm, and then returning to the step 25.

At step S130, a configuration (i.e., a shape) of the balance block set capable of adjusting the eccentricity amount is designed according to the dynamic disk eccentric portion of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set. The eccentricity amount comprises: a second eccentricity of the balancing block set.

The eccentricity of the eccentric part of the movable disc is known and given, and the eccentricity refers to the eccentricity of the main balance weight and the auxiliary balance weight. The main balance block and the auxiliary balance block are respectively provided with a movable mass block, and along with the increase of the rotating speed, the movable mass moves outwards along the guide rail in the radial direction under the action of self centrifugal force, so that the eccentric quantity of the main balance block and the auxiliary balance block is changed.

In some embodiments, designing the configuration (i.e. shape) of the balance block set capable of adjusting the eccentricity amount according to the dynamic disc eccentric portion of the scroll compressor and the shaft system deflection caused by the centrifugal force of the balance block set in step S130 includes the following two design aspects:

the first design aspect: and designing the configuration of the main balance weight. Wherein the configuration of the main balance weight comprises: the main weight body 26, the main weight cover 24 mounted on the main weight body 26, and the main weight mass assembly disposed in the main weight cover 24.

In a second design aspect: and designing the configuration of the secondary balance weight. Wherein the configuration of the secondary weight comprises: the secondary weight body 36, a secondary weight cover 34 mounted on the secondary weight body 36, and a secondary weight mass assembly disposed in the secondary weight cover 34.

The main balance weight mass component and the auxiliary balance weight mass component can adjust the eccentric amount.

the third step: and designing the configurations of a main balance block and an auxiliary balance block which can adjust the eccentricity.

FIG. 8 is a schematic view of the assembly structure of the shafting with the main balance weight and the auxiliary balance weight according to the present invention. FIG. 8 is an assembly view of the balance block with adjustable eccentricity on the shaft system, in the shaft system assembly structure with the main balance block and the auxiliary balance block, comprising: the eccentric part 1, the main balance weight 2 with adjustable eccentric amount, the auxiliary balance weight 3 with adjustable eccentric amount and the motor rotor 4.

As shown in fig. 8, the adjustable eccentric balancing block set includes: the main balance weight 2 with adjustable eccentricity and the auxiliary balance weight 3 with adjustable eccentricity. On the axis, the main balance weight 2 with adjustable eccentricity and the auxiliary balance weight 3 with adjustable eccentricity are distributed on two sides of the motor rotor 4.

In some embodiments, a main-weight mounting groove and a first guide rail 25 are provided in the main-weight cover 24. The first guide rail 25 is disposed in a hole formed between the main-weight cover 24 and the main weight. The guide rail is arranged at the middle position of the cover plate and the main balance block, but not at the bottom, see fig. 10; the holes for installing the guide rails are arranged on the cover plate in half and on the balance block in half.

The primary counterbalancing mass assembly is movable along the first guide rail 25. The guide rail is mounted in a hole formed by the cover plate and the main balance block, and the mass block can move on the guide rail.

The primary counterbalance mass assembly comprising: a first wave spring 21, a first movable mass 22 and a first damping layer 23. The first movable mass 22 is disposed between the first wave spring 21 and the first damping layer 23.

Fig. 9 is a front view of the main weight of the present invention. Fig. 10 isbase:Sub>A right side sectional view of the main weight of the present invention, specifically,base:Sub>A sectional view along the directionbase:Sub>A-base:Sub>A in fig. 9. FIG. 11 is a schematic three-dimensional structure of the main weight of the present invention. The main balance weight 2 with adjustable eccentricity is shown in fig. 9, 10 and 11.

As shown in fig. 9, in the main weight, a first wave spring (i.e., the wave spring of the main weight) 21, a first movable mass (i.e., the movable mass of the main weight) 22, and a first damping layer (i.e., the first damping layer of the main weight) 23 stuck on the first movable mass are provided. The first movable mass (i.e., the movable mass of the primary weight) 22 is located between the first wave spring (i.e., the wave spring of the primary weight) 21 and the first damping layer (i.e., the first damping layer of the primary weight) 23 stuck on the first movable mass.

As shown in fig. 10, the main weight is provided with a main weight cover 24, a first guide rail (i.e., a guide rail of the main weight) 25, and a main weight body 26. The first guide rail (i.e., the guide rail of the main weight) 25 is provided between the main-weight cover 24 and the main-weight main body 26.

As shown in fig. 11, the main weight is provided with a main weight cover 24, first screw holes (i.e., screw holes of the main weight) 27, and a main weight main body 26. The main weight cover 24 is provided on the main weight body 26, and the first screw hole (i.e., the screw hole of the main weight) 27 is provided on the main weight cover 24.

At low speed, the movable mass block is pressed at the bottom of the groove by the pretightening force of the spring, the damping layer prevents the impact noise of the movable mass and the bottom of the groove, and the mass and the eccentric quantity of the main balance block and the auxiliary balance block meet the force and moment equation (1). At high speed, the movable mass block starts to compress the spring to move towards the direction of increasing the eccentric amount under the action of centrifugal force, so that the adjustable eccentric amount of the main balance block and the auxiliary balance block is realized.

The secondary counterbalancing mass assembly comprising: the auxiliary weight cover 34 is provided with an auxiliary weight mounting groove and a second guide rail 35. The second guide rail 35 is disposed in a hole formed between the sub-weight cover 34 and the sub-weight. The guide rail is in the middle position of the cover plate and the auxiliary balance block, not at the bottom, see fig. 13; the holes for installing the guide rails are arranged on the cover plate in half and on the balance block in half.

The secondary counterbalancing mass assembly is movable along the second guide rail 35. The guide rail is arranged in a hole formed by the cover plate and the auxiliary balance block, and the mass block can move on the guide rail.

The secondary counterbalancing mass assembly comprising: a second wave spring 31, a second movable mass 32 and a second damping layer 33. The second movable mass 32 is disposed between the second wave spring 31 and the second damping layer 33.

Fig. 12 is a front view of the auxiliary weight according to the present invention. Fig. 13 is a right side sectional view of the auxiliary weight of the present invention, specifically, a sectional view along the direction B-B in fig. 12. FIG. 14 is a schematic three-dimensional structure of a secondary weight according to the present invention. The adjustable eccentric auxiliary weight 3 is shown in fig. 12, 13 and 14. In the examples shown in fig. 8 to 14, the movable mass, the guide rail, the spring, and the damping layer are added on the basis of the basic configuration of the weight.

The guide rail has the following functions: on one hand, the movable mass block is ensured to move along the balance block in the radial direction, and the guide effect is achieved; another aspect is to reduce friction as the movable mass moves.

As shown in fig. 12, in the adjustable eccentric sub-weight 3, a second wave spring (i.e., a wave spring of the sub-weight) 31, a second movable mass (i.e., a movable mass of the sub-weight) 32, and a second damping layer (i.e., a damping layer of the sub-weight) 33 bonded to the second movable mass are provided. A second movable mass (i.e., a movable mass of the sub-weight) 32 is located between the second wave spring (i.e., a wave spring of the sub-weight) 31 and a second damping layer (i.e., a damping layer of the sub-weight) 33 bonded to the second movable mass.

As shown in fig. 13, the adjustable eccentric auxiliary weight 3 is provided with an auxiliary weight cover 34, a second guide rail (i.e., a guide rail of the auxiliary weight) 35, and an auxiliary weight main body 36. The second guide rail (i.e., the guide rail of the sub-weight) 35 is provided between the sub-weight cover 34 and the sub-weight main body 36.

As shown in fig. 14, in the adjustable eccentric sub-weight 3, a second screw hole (i.e., a screw hole of the sub-weight) 37 is provided in the sub-weight cover plate 34.

The structure of the designed main balance weight is shown in fig. 9 to 11, the structure of the designed auxiliary balance weight is shown in fig. 12 to 14, and the assembly drawing of the whole crankshaft is shown in fig. 8 according to the shafting deflection curve caused by the centrifugal force of the movable disc eccentric part, the main balance weight and the auxiliary balance weight.

At low speed, the movable mass block is pressed on the damping layer by the spring, and the mass and the eccentric amount of the main balance block and the auxiliary balance block at the moment meet the force and moment balance. At high speed, the deflection of the shafting is increased due to the rapid increase of the centrifugal force of the balance block, and the deflection of the shafting can be reduced due to the fact that the movable mass block moves outwards in the radial direction under the action of the centrifugal force. By calculating and matching the mass and the spring of the movable mass block in the main balance block and the auxiliary balance block, the deflection of the shafting can be greatly reduced, and the force and the moment balance can be kept. So, can low-speed balance, can realize the balance under the less amount of deflection at high speed again, prevent to take place the unbalanced vibration noise of low-speed big and the high problem of eccentric wear and big noise that the too big amount of deflection arouses at high speed.

At step S140, based on the force balance relationship and the moment balance relationship at the second set speed, in combination with the basic parameters, the structural parameters of the balancing block set capable of adjusting the eccentricity are designed. The second set speed is greater than the first set speed. A second set speed, such as a high speed.

The invention provides a balance block design method considering shafting deflection and a balance block group thereof, in particular to a balance block design method considering deflection, namely a design method for reducing shafting deflection by a balance block.

Therefore, the design method of the deflection-considered adjustable eccentric amount balance block group provided by the scheme of the invention solves the problem that low-speed balance and high-speed balance in the design method in the related scheme can not be met at the same time, realizes the large inhibition of shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring the low-speed balance, and does not need to greatly change the layout and the support structure of the shafting.

In some embodiments, the specific process of designing the structural parameters of the balancing block set capable of adjusting the eccentricity amount based on the force balance relationship and the moment balance relationship at the second set speed in step S140 in combination with the basic parameters is as follows for exemplary description.

The following further describes a specific process of designing the structural parameters of the balancing block set capable of adjusting the eccentricity in step S140, with reference to a flowchart of an embodiment of designing the structural parameters of the balancing block set capable of adjusting the eccentricity in the method of the present invention shown in fig. 4, including: step S410 and step S420.

Step S410, determining a force balance relation and a moment balance relation at a second set speed according to the formula (3):

wherein L is _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the rotor of the machine, delta _p Deflection at the position of the center of mass of the main balance weight, delta _a Is the deflection of the position of the mass center of the auxiliary balance block delta _m The deflection of the center of mass position of the motor rotor.

Step S420, determining a structural parameter of the balancing block set capable of adjusting the eccentricity according to the basic parameter and the formula (3).

the fourth step: and (3) iteratively designing the structural parameters of the main balance block and the auxiliary balance block with adjustable eccentricity.

The main balance block and the auxiliary balance block with variable eccentricity need to satisfy the equation (1) at low speed and need to adjust the eccentricity e at high speed _p 、e _a And the force and moment balance equation considering deflection at high speed is satisfied:

in the formula (3), L _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the motor rotor 4. When the motor rotor 4 has deflection, unbalance is generated.

Due to the mass m of the main balance weight _z Mass m of auxiliary balance block _f The mass and the eccentricity of the balance weight are influenced by the groove determined by the groove, the spring stiffness kz of the main balance weight and the spring stiffness k of the auxiliary balance weight _f The eccentricity of the balance blocks at high speed is influenced, the structural parameters of the main balance block and the auxiliary balance block which meet the requirements of low-speed balance and high-speed balance and can adjust the eccentricity can be obtained by correlating the quantity to be solved with the structural parameters and then iteratively solving the equation (1) and the equation (3).

As for the iterative process, firstly, the preliminary main balance block and auxiliary balance block structures including movable masses, springs and the like can be optimized by solving the equation (1) as constraint according to the assembly space and process requirements; and then calculating to obtain the shafting deflection, then substituting the shafting deflection into equation (2), if the shafting deflection does not meet the error, adjusting the mass and the spring stiffness of the movable mass block, and entering the next iteration again until the low-speed and high-speed balance are met as much as possible.

The iterative process can be realized manually according to the experience of the designer, and can also be realized automatically by integrating the experience of the designer into an iterative program.

The formula (3) ensures the force and moment balance of the shafting at high speed, and considers the shafting deflection and the adjustable eccentricity, the formula 1 is a force balance equation, and the formula 1 is a moment balance equation. The effect of the device is to ensure the force and moment balance at high speed, and also to match the movable mass and the spring of the main balance block and the auxiliary balance block, so as to greatly reduce the deflection of the shafting. The deflection in the formula (3) is calculated by the formula (2), the parameters of the balance block are obtained by the formula (1), and the parameters are iteratively modified in the formula (1), the formula (2) and the formula (3) for multiple times in consideration of structural limitation and process, so that the optimized structural parameters are obtained.

The scheme of the invention adopts a balance block design method considering deflection and an adjustable eccentricity balance block structure matched with the balance block design method, solves the problems of overlarge shafting deflection caused by high-speed unbalanced force of the balance block, and further generates eccentric wear and large vibration noise, and can improve the bearing durability at high speed and reduce the vibration noise of the shafting.

In the related scheme, the design device of the balance block group does not consider the deflection, only considers the static force and moment balance, and does not have the design device of the balance block group with the adjustable eccentricity. By adopting the design flow shown in fig. 6, the balance of force and moment at low speed can be realized, and the shafting deflection caused by the centrifugal force of the balance block is greatly inhibited by adjusting the eccentric amount at high speed, wherein the eccentric amount is adjusted because the movable mass block moves outwards in the radial direction under the action of the centrifugal force. Therefore, the balance can be realized at low speed, the balance under smaller deflection at high speed can be realized, and the problems of eccentric wear and large noise caused by large vibration noise of low-speed unbalance and overlarge deflection at high speed are prevented.

In the above embodiment, the shape of the movable mass, the type and shape of the spring can be adjusted according to actual conditions, so that the arrangement mode of the movable mass is more flexible.

In the above embodiment, the movable mass may not have an adhesive damping layer underneath. That is, the damping layer may not be attached under the movable mass block, but directly attached in the groove accommodating the movable mass block, contacting with the movable mass block, but not directly attached, so that the movable mass block is more flexibly and conveniently disposed.

In summary, in the solution of the present invention, a design method of the balance weight considering the deflection is provided to design the structural parameters of the combination of the main balance weight and the auxiliary balance weight capable of adjusting the eccentricity.

In order to reduce the deflection at high speed, the invention provides the balance block and the auxiliary balance block which are matched with the design method and can adjust the eccentricity, and simultaneously, the balance block is made into a split structure in the movable mass block, so that the assembly problem is solved. Some schemes have no protection function, and because of a single balance block, the problem of reducing the deflection of the shaft system at high speed cannot be solved, and the technical problem that the assembly cannot be carried out exists. The other proposal is also used for reducing the shafting deflection at high speed, but the technical means is completely different from the proposal of the invention, and the proposal adopts that a balance weight combination is added and the deflection caused by the original balance weight combination is mutually offset. The other schemes solve the problem of reducing the deflection of the shafting at high speed, adopt and expand the space of the upper bracket, shorten the action distance of the main balance weight, reduce the deflection, and the technical means is completely different from the scheme of the invention.

As shown in fig. 10, the split structure is a structure in which the movable mass-containing portion of the weight is split into a cover plate 24 and a main weight body 26 as shown in fig. 10. The part is split to install the movable mass, and during installation, the spring, the movable mass block, the damping layer and the guide rail are firstly assembled, then the guide rail is placed in a cylindrical hole formed by the cover plate and the main balance block, and then a screw is screwed on the outside, wherein the screw hole is shown as a first screw hole 27 in fig. 11.

By adopting the technical scheme of the embodiment, the balance block group with the adjustable eccentric amount is designed under the condition of considering the shafting deflection, and the shafting deflection caused by the centrifugal force of the balance block at high speed is greatly inhibited under the condition of ensuring low-speed balance by utilizing the balance block group with the adjustable eccentric amount. Therefore, by designing the balance block considering the deflection of the shaft system, the balance block is utilized to inhibit the deflection of the crankshaft when the scroll compressor is at a high speed, the bearing endurance is prevented from being reduced and the shaft system is prevented from generating larger vibration noise due to the deflection of the crankshaft, and the working performance of the scroll compressor is ensured.

According to the embodiment of the invention, a device for designing the balancing block group corresponding to the method for designing the balancing block group is also provided. Referring to fig. 5, a schematic diagram of an embodiment of the apparatus of the present invention is shown. The balance block group can be applied to the scroll compressor. The balancing block group comprises: a primary weight and a secondary weight. The design device of the balancing block group comprises: and designing a unit.

The design unit is configured to design basic parameters of the balancing block group based on the force balance relation and the moment balance relation at a first set speed. A first set speed, such as a low speed. The specific function and processing of the design unit are shown in step S110.

In some embodiments, the designing unit, based on the force balance relationship and the moment balance relationship at the first set speed, designs the basic parameters of the balancing block set, including:

the design unit is specifically further configured to determine a force balance relationship and a moment balance relationship at a first set speed according to equation (1):

wherein m is _p 、e _p Mass and eccentricity of the main balance weight, m _a 、e _a Mass and eccentricity of the auxiliary balance weight, m _e 、e _e Respectively mass and eccentricity of the eccentric portion, L _p 、L _a The distances from the mass center of the main balance block and the mass center of the auxiliary balance block to the mass center of the eccentric part are respectively. The specific function and processing of the design unit are also referred to in step S210.

The design unit is specifically further configured to determine, in combination with a structural parameter of the basic configuration of the balancing block set, and a force balance relationship and a moment balance relationship at a first set speed, a mass and an eccentric amount of the main balancing block, and a mass and an eccentric amount of the auxiliary balancing block, as basic parameters of the balancing block set. The specific function and processing of the design unit are also referred to in step S220.

FIG. 6 is a schematic flow chart illustrating an embodiment of a deflection-considered weight design apparatus according to the present invention. The design flow of the balance block design device considering the deflection provided by the scheme of the invention is shown in fig. 6, firstly, at a low speed, the mass and the eccentric amount of the main balance block and the auxiliary balance block are designed according to the force balance and the moment balance, and then at a high speed, the force balance and the moment balance at the low speed and the force balance and the moment balance considering the deflection at the high speed are simultaneously satisfied by adjusting the eccentric amount of the main balance block and the auxiliary balance block. Specifically, as shown in fig. 6, the proposed deflection-considered weight design device according to the present invention includes:

And 14, satisfying low-speed balance and considering deflection height balance, and iteratively designing the structures of the main balance block and the auxiliary balance block with adjustable eccentricity.

In more detail, referring to the example shown in fig. 6, the proposed design of the balance weight considering deflection according to the present invention comprises the following main steps:

In the related scheme, a device is designed to design a balance block structure, and an equation which needs to satisfy force balance and moment balance at low speed is shown as a formula (1):

Based on the basic configuration (such as basic shape) of the main balance weight and the auxiliary balance weight, the mass m of the main balance weight can be measured _p Eccentricity e of the main balance weight _p Mass m of auxiliary balance block _a Eccentricity e of the auxiliary balance block _a The method is associated with the structural parameters, and m is obtained based on the optimization targets such as minimum quality and the like on the premise of meeting the formula (1) _p 、e _p 、m _a 、e _a The value of (c). The structural parameters, such as the outer diameter and the inner diameter of the basic configuration of the main balance weight and the auxiliary balance weight, are the same.

The design unit is further configured to determine a dynamic disc eccentric portion of the scroll compressor and a shafting deflection caused by a centrifugal force of the balance block group. The specific function and processing of the design unit are also referred to as step S120.

In some embodiments, the design unit, determining a dynamic disc eccentric of the scroll compressor and a shafting deflection caused by a centrifugal force of the balance block set, comprises: the design unit is specifically configured to couple iterative shafting deflection and bearing stiffness under the deflection with each other according to formula (2), and iteratively converge to calculate shafting deflection caused by centrifugal force of the dynamic disc eccentric part and the balance block group:

wherein u is _{dis_i} 、u _{dis_i+1} The axis deflection of the iteration step and the next iteration step, alpha is an iteration relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector. The centrifugal force of the balancing block group comprises: the centrifugal force of the primary weight, and the centrifugal force of the secondary weight.

Referring to the example shown in fig. 6, the proposed design of balance weight considering deflection in the solution of the present invention comprises the following main steps:

The calculation flow of the shafting deflection under the action of the centrifugal force is shown in figure 7, the device mutually couples the iterative shafting deflection and the bearing rigidity under the deflection, and iteratively converges to calculate the shafting deflection caused by the centrifugal force of the eccentric part of the dynamic disc, the main balance block and the auxiliary balance block, and the main iterative formula is as follows:

wherein u is _{dis_i} 、u _{dis_i+1} The axis system deflection of the iteration step and the next iteration step, alpha is an iteration relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector.

If the iterative convergence meets the set error, the deflection delta at the position of the mass center of the main balance block can be obtained _p And the deflection delta of the center of mass position of the auxiliary balance block _a And the deflection delta at the position of the mass center of the motor rotor _m And the deflection delta at the position of the eccentric part center of mass _e 。

The formula (2) is an iterative formula of shafting deflection calculation, because the compressor shafting contains the sliding bearing, the deflection is influenced by the rigidity and the damping of the sliding bearing, and simultaneously the rigidity and the damping of the sliding bearing are influenced by the deflection, if the shafting deflection under the action of external load needs to be solved, the axial deflection calculation can be realized by iterative calculation, and the specific flow is shown in fig. 7. The shafting deflection formed by assembling the structure calculated by the formula (1) under the centrifugal load of the main balance block and the auxiliary balance block of the compressor can be calculated by the formula (2).

In some embodiments, the designing unit, which couples the iterative shafting deflection and the bearing stiffness under the deflection to each other, and iteratively converges and calculates the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group, includes:

the design unit is specifically further configured to input structural parameters, material parameters, and external load of a shaft of the scroll compressor, a position and structural parameters of a bearing of the scroll compressor, and calculate an allowable maximum iteration step number, calculation accuracy, and an initial value of deflection of the shaft system. The specific function and processing of the design unit are also referred to in step S310.

The design unit is further configured to build a finite element model of a shaft of the scroll compressor, resulting in an overall stiffness matrix of the shaft. Obtaining a load vector according to the finite element model of the shaft and the external load; and calculating to obtain the initial value of the rigidity of the sliding bearing of the scroll compressor based on the initial value of the deflection. The specific function and processing of the design unit are also referred to in step S320.

The design unit is specifically configured to couple the integral stiffness array of the shaft and the initial value of the stiffness of the sliding bearing to form a system stiffness array. And processing the system stiffness array and the load vector before nonlinear iteration to obtain the deflection of the shaft. The specific function and processing of the design unit are also referred to in step S330.

The design unit is specifically configured to output the deflection of the shaft, the rigidity of each bearing and the number of damping iterations to determine the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group if the deflection of the shaft reaches the calculation accuracy within the allowed maximum iteration step number. The specific function and processing of the design unit are also referred to in step S340.

Fig. 7 is a schematic flow chart of an embodiment of a device for calculating the shafting deflection in the balance weight design apparatus according to the present invention. Fig. 7 is a schematic flow chart of the shafting deflection calculation device in the second step in fig. 6. As shown in fig. 7, the device for calculating the shafting deflection comprises:

And step 22, establishing a finite element model of the vertical shaft based on the Timoshenko beam unit to obtain an integral rigidity matrix of the shaft.

The Timoshenko beam is a beam capable of considering shear deformation, and displacement and section rotation angles of the Timoshenko beam are independently interpolated and are not obtained by derivatives of displacement.

And 23, obtaining a load vector according to the finite element model of the shaft and the external load.

And 26, preprocessing the system stiffness array and the load vector before nonlinear iteration.

And 27, solving to obtain the deflection of the shaft.

And step 28, judging whether the deflection meets the set precision: if yes, the deflection of the output shaft, the rigidity of each bearing and the damping iteration times are carried out. Otherwise, step 29 is performed.

Step 29, judging the number of iteration steps (i.e. whether the number of iterations exceeds a set value): if yes, ending the shafting deflection calculation process. Otherwise, according to the nonlinear iterative algorithm, calculating a new deflection value, calculating each bearing load, calculating each bearing stiffness, and then returning to the step 25.

The design unit is further configured to design the configuration (i.e. shape) of the balance block group capable of adjusting the eccentricity amount according to the dynamic disc eccentric part of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block group. The eccentricity amount comprises: a second eccentricity of the balancing block set. The specific function and processing of the design unit are also referred to in step S130.

In some embodiments, the design unit designs the configuration (i.e. shape) of the balance block group capable of adjusting the eccentricity amount according to the dynamic disc eccentric part of the scroll compressor and the shaft system deflection caused by the centrifugal force of the balance block group, and includes the following two design aspects:

the first design aspect: the design unit is particularly configured to design the configuration of the main weight. Wherein the configuration of the main balance weight comprises: the main balance weight assembly comprises a main balance weight body 26, a main balance weight cover plate 24 arranged on the main balance weight body 26, and a main balance weight mass component arranged in the main balance weight cover plate 24.

In a second design aspect: the design unit is specifically further configured to design a configuration of the secondary weight. Wherein the configuration of the secondary weight comprises: the secondary weight body 36, a secondary weight cover 34 mounted on the secondary weight body 36, and a secondary weight mass assembly disposed in the secondary weight cover 34.

Referring to the example shown in fig. 6, the proposed design of the balance weight considering deflection of the present invention includes the following main steps:

FIG. 8 is a schematic view of the assembly structure of the shafting with the main balance weight and the auxiliary balance weight according to the present invention. Fig. 8 is an assembly diagram of the balance block set with adjustable eccentricity on the shaft system, in the assembly structure of the shaft system equipped with the main balance weight and the auxiliary balance weight, including: the eccentric part 1, the main balance weight 2 with adjustable eccentric amount, the auxiliary balance weight 3 with adjustable eccentric amount and the motor rotor 4.

In some embodiments, a main-weight mounting groove and a first guide rail 25 are provided in the main-weight cover 24. The first guide rail 25 is disposed in a hole formed between the main-weight cover 24 and the main weight.

The primary counterbalancing mass assembly is movable along the first guide rail 25.

As shown in fig. 9, in the main weight, a first wave spring (i.e., the wave spring of the main weight) 21, a first movable mass (i.e., the movable mass of the main weight) 22, and a first damping layer (i.e., the first damping layer of the main weight) 23 bonded to the first movable mass are provided. The first movable mass (i.e., the movable mass of the primary weight) 22 is located between the first wave spring (i.e., the wave spring of the primary weight) 21 and the first damping layer (i.e., the first damping layer of the primary weight) 23 stuck on the first movable mass.

As shown in fig. 10, the main weight is provided with a main weight cover 24, a first guide rail (i.e., a guide rail of the main weight) 25, and a main weight body 26. The first guide rail (i.e., the guide rail of the main weight) 25 is provided between the main weight cover 24 and the main weight body 26.

As shown in fig. 11, the main weight is provided with a main weight cover 24, first screw holes (i.e., screw holes of the main weight) 27, and a main weight main body 26. The main weight cover 24 is disposed on the main weight body 26, and the first screw hole (i.e., the screw hole of the main weight) 27 is disposed on the main weight cover 24.

At low speed, the movable mass block is pressed at the bottom of the groove by the pretightening force of the spring, the damping layer is used for preventing the movable mass block and the impact noise at the bottom of the groove, and the mass and the eccentric quantity of the main balance block and the auxiliary balance block meet the force and moment equation (1). At high speed, the movable mass block starts to compress the spring to move towards the direction of increasing the eccentric amount under the action of centrifugal force, so that the adjustable eccentric amount of the main balance block and the auxiliary balance block is realized.

The secondary counterbalancing mass assembly comprising: the auxiliary weight cover 34 is provided with an auxiliary weight mounting groove and a second guide rail 35. And the second guide rail 35 is arranged in a hole formed between the auxiliary balance weight cover plate (34) and the auxiliary balance weight.

The secondary counterbalancing mass assembly is movable along the second guide rail 35.

The secondary counterbalance mass assembly comprising: a second wave spring 31, a second movable mass 32 and a second damping layer 33. The second movable mass 32 is disposed between the second wave spring 31 and the second damping layer 33.

Fig. 12 is a schematic front view of a secondary balance weight according to the present invention. Fig. 13 is a right side sectional view of the auxiliary weight of the present invention, specifically, a sectional view along the direction B-B in fig. 12. FIG. 14 is a schematic three-dimensional structure of a secondary balance weight according to the present invention. The adjustable eccentric auxiliary weight 3 is shown in fig. 12, 13 and 14. In the examples shown in fig. 8 to 14, the movable mass, the guide rail, the spring, and the damping layer are added on the basis of the basic configuration of the weight.

As shown in fig. 13, the adjustable eccentric sub-weight 3 is provided with a sub-weight cover 34, a second guide rail (i.e., a guide rail of the sub-weight) 35, and a sub-weight main body 36. The second guide rail (i.e., the guide rail of the sub-weight) 35 is provided between the sub-weight cover 34 and the sub-weight main body 36.

At low speed, the movable mass block is pressed on the damping layer by the spring, and the mass and the eccentric amount of the main balance block and the auxiliary balance block at the moment meet the force and moment balance. At high speed, the deflection of the shafting is increased due to the rapid increase of the centrifugal force of the balance block, and the deflection of the shafting can be reduced due to the fact that the movable mass block moves outwards in the radial direction under the action of the centrifugal force. By calculating and matching the mass and the spring of the movable mass block in the main balance block and the auxiliary balance block, the deflection of the shafting can be greatly reduced, and the force and the moment balance can be kept. Therefore, the balance device can realize low-speed balance and balance under smaller deflection at high speed, and prevent the problems of eccentric wear (namely shaft abrasion caused by overlarge shafting deflection due to high-speed unbalanced force of the balance block) and large noise caused by large low-speed unbalanced vibration noise and overlarge deflection at high speed.

The design unit is further configured to design the structural parameters of the balancing block group capable of adjusting the eccentricity amount based on the force balance relationship and the moment balance relationship at the second set speed in combination with the basic parameters. The second set speed is greater than the first set speed. A second set speed, such as high speed. The specific function and processing of the design unit are also referred to in step S140.

The invention provides a balance block design device considering shafting deflection and a balance block group thereof, in particular to a balance block design device considering deflection, namely a design device how the balance block reduces the shafting deflection.

Therefore, the design device of the adjustable eccentric amount balance block group considering deflection, provided by the scheme of the invention, solves the problem that low-speed balance and high-speed balance in the design device in the related scheme cannot be met at the same time, realizes the large inhibition of the deflection of the shaft system caused by the centrifugal force of the balance block at high speed under the condition of ensuring the low-speed balance, and does not need to greatly change the layout and the support structure of the shaft system.

In some embodiments, the designing unit, based on the force balance relationship and the moment balance relationship at the second set speed, and in combination with the basic parameters, designs the structural parameters of the balancing block set capable of adjusting the eccentricity amount, including:

the design unit is specifically further configured to determine a force balance relationship and a moment balance relationship at a second set speed according to equation (3):

wherein L is _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the rotor of the machine, delta _p Deflection at the position of the center of mass of the main balance weight, delta _a Is the deflection of the position of the mass center of the auxiliary balance block delta _m The deflection of the center of mass position of the motor rotor. The specific function and processing of the design unit are also referred to in step S410.

The design unit is specifically further configured to determine a structural parameter of the balancing block set capable of adjusting the eccentricity amount according to the basic parameter and the formula (3). The specific function and processing of the design unit are also referred to in step S420.

in the formula (3), L _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the motor rotor.

The formula (3) ensures the force and moment balance of the shafting at high speed, and considers the shafting deflection and the adjustable eccentricity, the formula 1 is a force balance equation, and the formula 1 is a moment balance equation. The effect of the device is to ensure the balance of force and moment at high speed, and also to match the movable mass and the spring of the main balance block and the auxiliary balance block, thereby realizing the great reduction of the shafting deflection. The deflection in the formula (3) is calculated by the formula (2), the parameters of the balance block are obtained by the formula (1), and the parameters are iteratively modified in the formula (1), the formula (2) and the formula (3) for multiple times in consideration of structural limitation and process, so that the optimized structural parameters are obtained.

According to the scheme, the design device of the balance block considering deflection and the structure of the balance block with adjustable eccentricity matched with the design device are adopted, so that the problems of overlarge shafting deflection caused by high-speed unbalanced force of the balance block and further eccentric wear and large vibration noise are solved, the bearing durability at high speed can be improved, and the shafting vibration noise can be reduced.

In summary, in the solution of the present invention, a device for designing a balance weight considering deflection is provided to design a structural parameter of a combination of a main balance weight and an auxiliary balance weight capable of adjusting an eccentricity.

In order to reduce the deflection at high speed, the invention provides the balance block and the auxiliary balance block which are matched with a design device and can adjust the eccentricity, and simultaneously, the balance block is made into a split structure in the movable mass block, so that the assembly problem is solved. Some schemes have no protection function, and because of a single balance block, the problem of reducing the deflection of the shaft system at high speed cannot be solved, and the technical problem that the assembly cannot be carried out exists. The other proposal is also used for reducing the shafting deflection at high speed, but the technical means is completely different from the proposal of the invention, and the proposal adopts that a balance weight combination is added and the deflection caused by the original balance weight combination is mutually offset. The other scheme solves the problem of reducing the deflection of the shaft system at high speed, adopts the expansion of the upper bracket space, shortens the acting distance of the main balance block and reduces the deflection, and the technical means is completely different from the scheme of the invention.

Since the processes and functions implemented by the apparatus of this embodiment substantially correspond to the embodiments, principles and examples of the method, reference may be made to the related descriptions in the embodiments without being detailed in the description of this embodiment, which is not described herein again.

By adopting the technical scheme of the invention, the balance block group with adjustable eccentricity is designed under the condition of considering the shafting deflection, and the balance block group with adjustable eccentricity is utilized to realize the large-scale inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring the low-speed balance, solve the problem that the eccentricity of the balance block cannot be adjusted, realize the low-speed balance and realize the balance of considering the deflection at high speed.

According to the embodiment of the invention, a balancing block group corresponding to the design device of the balancing block group is also provided. The balance block group is obtained by the design method of the balance block group or the design device of the balance block group.

The scheme of the invention also provides a variable eccentric balancing block group matched with the design method, in particular to a balancing block group structure capable of realizing force and moment balance at low speed and height. By reducing the deflection generated by the crankshaft at high speed, the bearing durability is improved, the vibration noise of a shafting is reduced, and particularly the bearing durability is improved at high speed, and the vibration noise of the shafting is reduced. Therefore, the balance block structure with the adjustable eccentric amount solves the problem that the eccentric amount of the balance block cannot be adjusted, and can realize low-speed balance and balance considering deflection at high speed.

Since the processing and functions implemented by the balancing block set of this embodiment substantially correspond to the embodiments, principles, and examples of the foregoing apparatus, reference may be made to the related descriptions in the foregoing embodiments without being detailed in the description of this embodiment.

By adopting the technical scheme of the invention, the balance block group with the adjustable eccentricity is designed under the condition of considering the shafting deflection, and the balance block group with the adjustable eccentricity is utilized to simultaneously realize the great inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring the low-speed balance, and the bearing durability at high speed and the shafting vibration noise are improved and reduced by reducing the deflection generated by the crankshaft at high speed.

According to an embodiment of the present invention, there is also provided a storage medium corresponding to a method for designing a balancing block group, where the storage medium includes a stored program, and when the program runs, a device on which the storage medium is located is controlled to execute the method for designing a balancing block group described above.

Since the processing and functions implemented by the storage medium of this embodiment substantially correspond to the embodiments, principles, and examples of the foregoing method, reference may be made to the related descriptions in the foregoing embodiments without being detailed in the description of this embodiment.

By adopting the technical scheme of the invention, the balance block group with adjustable eccentricity is designed under the condition of considering the shafting deflection, and the balance block group with adjustable eccentricity is utilized to simultaneously realize the large inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring low-speed balance, and the bearing durability is improved and the vibration noise of the shafting is reduced by reducing the deflection generated by the crankshaft at high speed.

According to an embodiment of the present invention, there is also provided a processor corresponding to the method for designing a balancing block group, where the processor is configured to run a program, where the program executes the method for designing a balancing block group as described above.

Since the processing and functions implemented by the processor of this embodiment substantially correspond to the embodiments, principles, and examples of the foregoing method, reference may be made to the related descriptions in the foregoing embodiments without being detailed in the description of this embodiment.

By adopting the technical scheme of the invention, the balance block group with adjustable eccentricity is designed under the condition of considering the shafting deflection, and the balance block group with adjustable eccentricity is utilized to realize the large-scale inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring low-speed balance, thereby realizing the large-scale reduction of the shafting deflection and keeping the force and moment balance.

In summary, it is readily understood by those skilled in the art that the advantageous modes described above can be freely combined and superimposed without conflict.

The above description is only an example of the present invention, and is not intended to limit the present invention, and it is obvious to those skilled in the art that various modifications and variations can be made in the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the scope of the claims of the present invention.

Claims

1. A design method of a balance block group is characterized in that the balance block group can be applied to a scroll compressor; the balancing block group comprises: a primary balance weight and a secondary balance weight; the design method of the balancing block group comprises the following steps:

designing basic parameters of the balancing block group based on a force balance relation and a moment balance relation at a first set speed; the method comprises the following steps of designing basic parameters of the balancing block group based on a force balance relation and a moment balance relation under a first set speed, wherein the basic parameters comprise: determining a force balance relationship and a moment balance relationship at a first set speed according to equation (1):

wherein m is _p 、e _p Mass and eccentricity of the main balance weight, m _a 、e _a Mass and eccentricity of the auxiliary balance weight, m _e 、e _e Respectively mass and eccentricity of the eccentric portion, L _p 、L _a The distances from the mass center of the main balance block and the mass center of the auxiliary balance block to the mass center of the eccentric part are respectively; determining the mass and the eccentric amount of the main balancing block and the mass and the eccentric amount of the auxiliary balancing block as basic parameters of the balancing block set by combining the structural parameters of the basic configuration of the balancing block set and the force balance relationship and the moment balance relationship at a first set speed;

determining the shaft system deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group of the scroll compressor;

designing the configuration of the balancing block group capable of adjusting the eccentricity according to the eccentric part of the movable disc of the scroll compressor and the shafting deflection caused by the centrifugal force of the balancing block group; the eccentricity amount comprises: a second eccentricity of the balancing block set;

designing structural parameters of the balancing block group capable of adjusting the eccentricity based on the force balance relationship and the moment balance relationship at a second set speed in combination with the basic parameters; the second set speed is greater than the first set speed;

by designing the balance block group with adjustable eccentricity under the condition of considering the shafting deflection, the balance block group with adjustable eccentricity is utilized to realize the large inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring the low-speed balance.

2. The method for designing a balance block set of claim 1, wherein determining the dynamic disk eccentricity of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set comprises:

according to a formula (2), coupling iterative shafting deflection and bearing rigidity under the deflection, and calculating shafting deflection caused by centrifugal force of the dynamic disc eccentric part and the balance block group through iterative convergence:

wherein u is _{dis_i} 、u _{dis_i+1} The axis system deflection of the iteration step and the next iteration step, alpha is an iteration relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector; the centrifugal force of the balancing block set comprises: the centrifugal force of the primary weight, and the centrifugal force of the secondary weight.

3. The method for designing a balance block set according to claim 2, wherein the iterative shaft system deflection and the bearing stiffness under the deflection are coupled to each other, and the iterative convergence calculates the shaft system deflection caused by the centrifugal force of the dynamic eccentric part and the balance block set, and comprises:

inputting structural parameters, material parameters and external load of a shaft of the scroll compressor, the position and the structural parameters of a bearing of the scroll compressor, and calculating the allowable maximum iteration step number, the calculation precision and the initial value of the deflection of the shaft system;

establishing a finite element model of a shaft of the scroll compressor to obtain an overall stiffness matrix of the shaft; obtaining a load vector according to the finite element model of the shaft and the external load; calculating to obtain an initial value of the rigidity of the sliding bearing of the scroll compressor based on the initial value of the deflection;

coupling the integral rigidity array of the shaft and the initial value of the rigidity of the sliding bearing to form a system rigidity array; processing the system stiffness array and the load vector before nonlinear iteration to obtain the deflection of the shaft;

and within the allowed maximum iteration step number, if the deflection of the shaft reaches the calculation precision, outputting the deflection of the shaft, the rigidity of each bearing and the damping iteration times to determine the shafting deflection caused by the centrifugal force of the movable disc eccentric part and the balance block group.

4. The method for designing balance block set according to claim 1, wherein the configuration of the balance block set capable of adjusting eccentricity according to the dynamic disc eccentric portion of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set comprises:

designing the configuration of the main balance weight; wherein the configuration of the main balance weight comprises: a main counterweight body (26), a main counterweight cover plate (24) mounted on the main counterweight body (26), and a main counterweight mass assembly disposed in the main counterweight cover plate (24);

designing the configuration of the secondary balance weight; wherein the configuration of the secondary weight comprises: a secondary counterweight body (36), a secondary counterweight cover plate (34) mounted on the secondary counterweight body (36), and a secondary counterweight mass assembly disposed in the secondary counterweight cover plate (34);

the main balance weight mass component and the auxiliary balance weight mass component can adjust the eccentricity.

5. The method for designing a balancing block set according to claim 4, wherein a primary weight mounting groove and a first guide rail (25) are provided in the primary weight cover plate (24); the first guide rail (25) is arranged in a hole formed between the main balance weight cover plate (24) and the main balance weight;

the main balance weight mass component can move along a first guide rail (25);

the primary counterbalance mass assembly comprising: a first wave spring (21), a first movable mass (22) and a first damping layer (23); -the first movable mass (22) arranged between the first wave spring (21) and the first damping layer (23);

the secondary counterbalance mass assembly comprising:

an auxiliary balance block mounting groove and a second guide rail (35) are arranged on the auxiliary balance block cover plate (34); the second guide rail (35) is arranged in a hole formed between the auxiliary balance weight cover plate (34) and the auxiliary balance weight;

the secondary balance weight mass component can move along a second guide rail (35);

the secondary counterbalancing mass assembly comprising: a second wave spring (31), a second movable mass (32) and a second damping layer (33); the second movable mass (32) disposed between the second wave spring (31) and the second damping layer (33).

6. The method for designing a balance block set according to claim 1, wherein the designing a structural parameter of the balance block set capable of adjusting the eccentricity amount based on the force balance relationship and the moment balance relationship at the second set speed in combination with the basic parameter comprises:

and (3) determining the force balance relation and the moment balance relation at the second set speed according to the formula (3):

wherein L is _m Is the distance from the center of mass of the motor rotor to the center of mass of the eccentric part, m _m Is the mass of the rotor of the machine, delta _p Deflection at the position of the center of mass of the main balance weight, delta _a Is the deflection of the position of the mass center of the auxiliary balance block delta _m The deflection is the position of the center of mass of the motor rotor;

and determining the structural parameters of the balancing block group capable of adjusting the eccentricity according to the basic parameters and the formula (3).

7. A design device of a balance block group is characterized in that the balance block group can be applied to a scroll compressor; the balancing block group comprises: a primary balance weight and a secondary balance weight; the design device of the balancing block group comprises:

a design unit configured to design basic parameters of the balance block group based on a force balance relationship and a moment balance relationship at a first set speed; the design unit is used for designing basic parameters of the balancing block group based on a force balance relation and a moment balance relation at a first set speed, and comprises the following steps: determining a force balance relationship and a moment balance relationship at a first set speed according to equation (1):

wherein m is _p 、e _p Mass and eccentricity of the main balance weight, m _a 、e _a Mass and eccentricity of the auxiliary balance weight, m _e 、e _e Respectively the mass and the eccentricity of the eccentric portion, L _p 、L _a The distances from the mass center of the main balance block and the mass center of the auxiliary balance block to the mass center of the eccentric part are respectively; structural parameters of basic configuration of the balancing block group are combined, and the speed is set at the first set speedDetermining the mass and the eccentricity of the main balancing block and the mass and the eccentricity of the auxiliary balancing block as basic parameters of the balancing block group;

the design unit is further configured to determine a dynamic disc eccentric portion of the scroll compressor and a shafting deflection caused by a centrifugal force of the balance block group;

the design unit is further configured to design the configuration of the balance block group capable of adjusting the eccentricity amount according to the dynamic disc eccentric part of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block group; the eccentricity amount comprises: a second eccentricity of the balancing block set;

the design unit is further configured to design a structural parameter of the balancing block group capable of adjusting the eccentricity amount based on a force balance relation and a moment balance relation at a second set speed in combination with the basic parameter; the second set speed is greater than the first set speed;

the balance block group with the adjustable eccentricity is designed under the condition of considering the shafting deflection, and the balance block group with the adjustable eccentricity is utilized to realize the large inhibition of the shafting deflection caused by the centrifugal force of the balance block at high speed under the condition of ensuring low-speed balance.

8. The balance block set design device of claim 7, wherein the design unit, determining the dynamic disc eccentricity of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set, comprises:

wherein u is _{dis_i} 、u _{dis_i+1} Shaft deflection, alp, for the present and lower iterationha is the iterative relaxation factor, K _shaft Is the overall stiffness matrix of the rotor, K _bearing Is a stiffness matrix of the bearing, F _external Is an external load vector; the centrifugal force of the balancing block set comprises: the centrifugal force of the primary weight, and the centrifugal force of the secondary weight.

9. The apparatus for designing a balance block set according to claim 8, wherein the design unit couples the iterative shafting deflection and the bearing stiffness under the deflection to each other, and iteratively converges the shafting deflection caused by the centrifugal force of the rotor eccentric portion and the balance block set, and comprises:

inputting structural parameters, material parameters and external load of a shaft of the scroll compressor, the position and structural parameters of a bearing of the scroll compressor, and calculating the maximum allowable iteration step number, calculation precision and initial value of deflection of the shaft system deflection;

10. The balance block set designing apparatus of claim 7, wherein the designing unit designs the configuration of the balance block set capable of adjusting the eccentricity amount according to the dynamic disc eccentric portion of the scroll compressor and the shafting deflection caused by the centrifugal force of the balance block set, comprising:

11. The balance block set designing apparatus according to claim 10, wherein a main balance weight mounting groove and a first guide rail (25) are provided in the main balance weight cover plate (24); the first guide rail (25) is arranged in a hole formed between the main balance weight cover plate (24) and the main balance weight;

the main balance weight mass component can move along a first guide rail (25);

the secondary counterbalancing mass assembly comprising:

12. The device for designing a balance block set according to claim 7, wherein the design unit, based on the force balance relationship and the moment balance relationship at the second set speed, in combination with the basic parameters, designs the structural parameters of the balance block set capable of adjusting the eccentricity amount, including:

13. A balancing block set, characterized in that the balancing block set is obtained by a method for designing a balancing block set according to any one of claims 1 to 6, or by an apparatus for designing a balancing block set according to any one of claims 7 to 12.

14. A storage medium, comprising a stored program, wherein when the program runs, a device in which the storage medium is located is controlled to execute the method for designing a balancing block set according to any one of claims 1 to 6.

15. A processor, characterized in that the processor is configured to run a program, wherein the program is configured to execute the method for designing a balancing block set according to any one of claims 1 to 6 when running.