Vibration reduction method and device for double balance weights and rotary Stirling refrigerator

Abstract

The invention provides a vibration reduction method and device for double balance weights and a rotary Stirling cryocooler, and belongs to the technical field of balance weight vibration reduction. The method comprises the steps that S1, an axis stress component is provided, and an eccentric component is installed on the axis stress component; s2, a first moving component and a second moving component are installed on the axis stress component, and the eccentric force of the first moving component, the eccentric force of the second moving component and the eccentric force of the eccentric component acting on the axis stress component are not coplanar; and S3, the first movement component and / or the second movement component are / is adjusted, so that the force and torque of the axis stress component in the radial direction are balanced. The double-balance-weight balance mechanism has the advantages that the double-balance-weight design is adopted, the balance of force and torque of an axis stress component in the radial direction is achieved, the problem that it is difficult for a single balance weight to balance the radial force and torque on a rotating shaft at the same time is solved, vibration and noise generated by unbalanced radial torque are reduced, and the overall operation stability is improved.

Description

Technical Field

[0001] The invention relates to the technical field of counterweight vibration reduction, and in particular to a vibration reduction method and device for double-balance counterweights and a rotary Stirling refrigerator. Background Art

[0002] As a highly efficient and environmentally friendly refrigeration equipment, the precise design and dynamic balance of the internal mechanical structure of the Stirling refrigerator are crucial to its performance. Among them, the balancing weight device is one of the important components to ensure the stability, balance and reliability of the whole machine.

[0003] At present, the existing balancing weight device mainly adopts a single balancing weight structure, which is usually designed based on a single flywheel or a single eccentric weight block with large mass and large moment of inertia. Figure 1 and Figure 2 The figure shows a balancing weight device based on a single flywheel, in which the flywheel mass center, the eccentric shaft mass center and the rotating shaft mass center are often not in the same plane, that is, not coplanar. Figure 3 and Figure 4 It shows the eccentric force of a single flywheel and an eccentric shaft acting on the rotating shaft. Figure 4 In the figure, point O is the rotation center of the motor shaft, m a is the mass and position of the eccentric shaft on the rotating shaft. It rotates around point O at an angular velocity w. Its distance from point O is defined as r. a ; m1 is the mass and center of mass position of the compression piston, which is approximately linear reciprocating motion on the y-axis; m2 is the mass and center of mass position of the expansion piston, which is approximately linear reciprocating motion on the x-axis; m b To balance the mass and center of mass of a counterweight device (such as a flywheel or a counterweight), it rotates around point O at an angular velocity w, and its distance from point O is defined as r b , its force balance formula is:

[0004]

[0005] Among them, m a Indicates the mass of the eccentric shaft; m b represents the flywheel mass; r a Indicates the eccentricity of the eccentric shaft; r b represents the eccentricity of the flywheel; m1 represents the mass of the expansion piston assembly; m2 represents the mass of the compression piston assembly; w represents the angular velocity; represents the expansion piston acceleration; represents the compression piston acceleration.

[0006] According to the above balance equation, by optimizing the flywheel mass m b and flywheel eccentricity r b , to achieve the balance of eccentric force in the axial direction of the rotating shaft.

[0007] However, due to the structural limitations of the Stirling refrigerator, the eccentric force generated by the single counterweight structure and the force generated by the eccentric shaft on the rotating shaft are not in the same plane, that is, they are not coplanar, which leads to an unbalanced torque on the rotating shaft in the radial direction, causing certain high-frequency vibration and noise interference to the entire machine, thereby affecting the overall performance of the Stirling refrigerator. Summary of the invention

[0008] In order to solve the above technical problems, the present invention provides a double balancing weight vibration reduction method; on the other hand, it also provides a double balancing weight device; on the other hand, it also provides a rotary Stirling refrigerator.

[0009] The technical problem solved by the present invention can be achieved by adopting the following technical solutions:

[0010] A first aspect of the present invention is to provide a vibration reduction method of a double balancing weight, comprising:

[0011] Step S1, providing an axial force bearing component, wherein an eccentric component is installed on the axial force bearing component;

[0012] Step S2, installing a first moving component and a second moving component on the axial force bearing component, wherein the eccentric forces of the first moving component, the second moving component and the eccentric component acting on the axial force bearing component are not coplanar;

[0013] Step S3, adjusting the first moving component and / or the second moving component to balance the force and moment of the axial force-bearing component in the radial direction.

[0014] Preferably, in step S3, the eccentric mass and the eccentricity of the center of mass of the first moving component and / or the second moving component are adjusted to balance the force and moment of the axially loaded component in the radial direction.

[0015] Preferably, the first moving component is a first flywheel, the first flywheel has a first eccentric mass, and the center of mass of the first flywheel is spaced from the center of mass of the axial force bearing component by a first center of mass eccentricity;

[0016] The second moving component is a second flywheel, the second flywheel has a second eccentric mass, and the center of mass of the second flywheel is spaced from the center of mass of the axial force bearing component by a second center of mass eccentricity;

[0017] The first eccentric mass and the second eccentric mass are the same or different, and the first center of mass eccentricity and the second center of mass eccentricity are different.

[0018] Preferably, the first moving member and the second moving member are located on both sides of the eccentric member.

[0019] Preferably, the first moving component and the second moving component are integrally formed.

[0020] A second aspect of the present invention is to provide a dual-balance counterweight device, comprising an axial force bearing member, an eccentric member being mounted on the axial force bearing member, and the device further comprising:

[0021] A first moving component is installed on the axial force bearing component;

[0022] The second moving component is installed on the axial force-bearing component, wherein the eccentric forces of the first moving component, the second moving component and the eccentric component acting on the axial force-bearing component are not coplanar, and the force and moment of the axial force-bearing component in the radial direction are balanced.

[0023] Preferably, the first moving component is a first flywheel, the first flywheel has a first eccentric mass, and the center of mass of the first flywheel is spaced from the center of mass of the axial force bearing component by a first center of mass eccentricity;

[0024] The second moving component is a second flywheel, the second flywheel has a second eccentric mass, and the center of mass of the second flywheel is spaced from the center of mass of the axial force bearing component by a second center of mass eccentricity;

[0025] The first eccentric mass and the second eccentric mass are the same or different, and the first center of mass eccentricity and the second center of mass eccentricity are different.

[0026] Preferably, the first moving member and the second moving member are located on both sides of the eccentric member.

[0027] Preferably, the first moving component and the second moving component are integrally formed.

[0028] A third aspect of the present invention is to provide a rotary Stirling refrigerator, comprising an axial force bearing component, on which an eccentric component and the double balancing weight device as described above are mounted.

[0029] The advantages or beneficial effects of the technical solution of the present invention are:

[0030] The present invention adopts a double balancing weight design to adjust the first moving component and / or the second moving component to achieve the balance of force and torque in the radial direction of the axially loaded component, thereby solving the problem that a single balancing weight is difficult to simultaneously take into account the balance of radial force and torque on the rotating shaft, thereby reducing the vibration and noise caused by unbalanced radial torque and improving the overall operation stability. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 It is a front view of a single balancing weight device in the prior art;

[0032] Figure 2 It is a left view of a single balancing weight device in the prior art;

[0033] Figure 3 It is a schematic diagram of force and moment analysis on a rotating shaft in the prior art;

[0034] Figure 4 It is a schematic diagram of the movement of simplified components of a refrigerator in the prior art;

[0035] Figure 5 It is a flow chart of a vibration reduction method of double balancing weights in a preferred embodiment of the present invention;

[0036] Figure 6 It is a front view of a double balancing weight device (separate type) in a preferred embodiment of the present invention;

[0037] Figure 7 This is a schematic diagram of force and moment analysis on the rotating shaft in a preferred embodiment of the present invention;

[0038] Figure 8 It is a front view of a double balancing weight device (integrated) in a preferred embodiment of the present invention.

[0039] Description of reference numerals:

[0040] 1. Axially loaded component; 2. Eccentric component; 3. First moving component; 4. Second moving component; A. Center of mass of rotating shaft; B. Center of mass of eccentric shaft; C. Center of mass of first flywheel; D. Center of mass of second flywheel. DETAILED DESCRIPTION

[0041] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0042] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments may be combined with each other.

[0043] The present invention will be further described below in conjunction with the accompanying drawings and specific embodiments, but they are not intended to limit the present invention.

[0044] In a preferred embodiment of the present invention, based on the above problems existing in the prior art, a vibration reduction method of a double balancing weight is provided. Figure 5 and Figure 6 As shown, including:

[0045] Step S1, providing an axial force bearing component 1, on which an eccentric component 2 is installed;

[0046] Step S2, installing the first moving component 3 and the second moving component 4 on the axial force bearing component 1, wherein the eccentric forces of the first moving component 3, the second moving component 4 and the eccentric component 2 acting on the axial force bearing component 1 are not coplanar;

[0047] Step S3, adjusting the first moving component 3 and / or the second moving component 4 to balance the force and moment of the axial force bearing component 1 in the radial direction.

[0048] Specifically, in response to the problem that the existing single flywheel cannot balance the radial force and torque on the steering shaft at the same time, in this embodiment, a double balancing weight design is adopted to adjust the first moving component 3 and / or the second moving component 4 to achieve the balance of force and torque in the radial direction of the axial force-bearing component 1, thereby solving the problem that a single balancing weight is difficult to balance the radial force and torque on the rotating shaft at the same time, thereby reducing the vibration and noise caused by the imbalance of radial torque and improving the overall operation stability.

[0049] Specifically, first, an axial force bearing member 1 is provided. In this embodiment, the axial force bearing member 1 is a rotating shaft. An eccentric member 2 is installed on the rotating shaft. Specifically, the eccentric member 2 is an eccentric shaft.

[0050] Next, the first moving component 3 and the second moving component 4 are installed on the rotating shaft. In this embodiment, the first moving component 3 is a first flywheel, and the second moving component 4 is a second flywheel. By designing two flywheels, the eccentric forces of the first flywheel, the second flywheel and the eccentric shaft acting on the rotating shaft are not on the same horizontal plane, that is, not coplanar.

[0051] In order to minimize the vibration of the whole structure, the balance between the force F and the moment T on the shaft needs to be satisfied, that is:

[0052] ∑F=0

[0053] ∑T=0

[0054] like Figure 7 As shown, on the rotating shaft, the force F in the radial direction can be expressed as:

[0055] F = F1-F2-F3;

[0056] Wherein, F1 represents the radial unbalanced force of the eccentric member 2 on the rotating shaft, including the combined force of the eccentric shaft, the expansion piston and the compression piston; F2 represents the centrifugal force generated by the first flywheel; and F3 represents the centrifugal force generated by the second flywheel.

[0057] On the rotating shaft, the moment T in the radial direction can be expressed as:

[0058] T = T1-T2;

[0059] Wherein, T1 represents the moment between the centrifugal force (F2) generated by the first flywheel and the radial unbalanced force (F1); T2 represents the moment between the force (F3) generated by the second flywheel and the radial unbalanced force (F1).

[0060] According to Newton's second law, force is the product of mass and acceleration of an object. Furthermore, torque is the product of force and lever arm, where the lever arm is the direction of the force and the perpendicular distance from the line of action of the force to the axis of rotation (or reference point).

[0061] From this, the theoretical balance formula of the double balance weight device can be derived, and its mathematical expression is as follows:

[0062] m 12 r 12 +m a r a -m b1 r b1 -m b2 r b2 =0

[0063] (m a12 r a12 l a12 -m b1 r b1 l b1 -m b2 r b2 l b2 ) 2 =0

[0064] Among them, m 12 represents the equivalent inertial force balance mass; r 12 Indicates the distance between the equivalent inertia center and the axis; m a represents the mass of the eccentric component 2; r a Represents the distance between the center of mass of the eccentric member 2 and the axis; m b1 represents the mass of the first flywheel; r b1 Represents the distance between the center of mass C of the first flywheel and the axis of the shaft; m b2 represents the mass of the second flywheel; r b2 Represents the distance between the mass center D of the second flywheel and the axis of the shaft; m a12 Indicates the equivalent mass of the radial centrifugal force on the shaft (m 12 and m a composition), that is, the equivalent inertial force balance mass m 12 and the mass m of the eccentric member 2 a The vector sum of a12 Indicates the distance between the center of mass of the equivalent mass and the axis; l a12represents the distance between the equivalent mass center and the reference point. In this embodiment, the position of the reference point can be customized. b1 Indicates the distance between the center of mass of the first flywheel and the reference point; l b2 represents the distance between the center of mass of the second flywheel and the reference point; w represents the angular velocity of the rotating shaft.

[0065] By adjusting the relative position of the two flywheels, that is, the relative reference distance l b1 , l b2 and adjust the mass m b1 、m b2 , while achieving force balance, the balance of torque is also achieved.

[0066] As a preferred embodiment, in step S3, the eccentric mass and the eccentricity of the center of mass of the first moving component 3 and / or the second moving component 4 are adjusted to balance the force and torque of the axially loaded component 1 in the radial direction.

[0067] Specifically, in this embodiment, by adjusting the mass m of the two flywheel balancing weight structures b1 、m b2 and the eccentricity of the center of mass, i.e. the relative reference distance l b1 , l b2 , achieving radial force and torque balance of the rotating shaft, thereby eliminating the vibration and noise caused by unbalanced radial force and torque.

[0068] As a preferred embodiment, the first moving component 3 is a first flywheel, the first flywheel has a first eccentric mass, and the center of mass C of the first flywheel is spaced from the center of mass of the axial force bearing component 1 by a first center of mass eccentricity;

[0069] The second moving component 4 is a second flywheel, the second flywheel has a second eccentric mass, and the center of mass D of the second flywheel is spaced from the center of mass of the axial force bearing component 1 by a second center of mass eccentricity;

[0070] The first eccentric mass and the second eccentric mass are the same or different, and the first center of mass eccentricity and the second center of mass eccentricity are different.

[0071] Specifically, in this embodiment, the interior or edge of the first flywheel and the second flywheel is specially designed to achieve uneven overall mass distribution, forming eccentric mass, for example, by adding mass to a part of the flywheel (such as adding an additional mass block) or removing part of the mass (such as slotting or drilling).

[0072] The eccentric distance of the center of mass is the straight-line distance between the center of mass of the flywheel and the center of mass A of the rotating shaft.

[0073] Furthermore, the first flywheel and the second flywheel may be of separate design or of integral design, and their structural form is not limited to cylindrical cutting. As long as their structure can produce eccentric mass and thus generate two sets of eccentric forces, and achieve the balance of force and torque through three (at least) non-coplanar eccentric forces, this core design concept belongs to the dual flywheel design idea of ​​the present invention.

[0074] As a preferred embodiment, the first moving component 3 and the second moving component 4 are located on both sides of the eccentric component 2 .

[0075] Specifically, in this embodiment, the two flywheels adopt a separate design, the two flywheels and the eccentric shaft sleeve are arranged on the rotating shaft, and the two flywheels are located on both sides of the eccentric shaft. The center of mass C of the first flywheel and the center of mass D of the second flywheel are not on the same horizontal plane, and the center of mass C of the first flywheel, the center of mass D of the second flywheel and the center of mass A of the rotating shaft and the center of mass B of the eccentric shaft are also not coplanar.

[0076] As a preferred embodiment, wherein Figure 8 As shown, the first moving component 3 and the second moving component 4 are integrally formed.

[0077] Specifically, in this embodiment, the two flywheels are of integral design, that is, the two flywheels are integrally formed, and the centers of mass of the two flywheels are not on the same horizontal plane, and the centers of mass of the two flywheels are not coplanar with the center of mass A of the rotating shaft and the center of mass B of the eccentric shaft.

[0078] The integral double flywheel balance weight structure is simple to assemble, compact in structure and has a wider range of applications.

[0079] The present invention also provides a double-balanced counterweight device, comprising an axial force bearing component 1, an eccentric component 2 is mounted on the axial force bearing component 1, and the device further comprises:

[0080] The first moving component 3 is installed on the axial force bearing component 1;

[0081] The second moving component 4 is installed on the axially loaded component 1, wherein the eccentric forces of the first moving component 3, the second moving component 4 and the eccentric component 2 acting on the axially loaded component 1 are not coplanar, and the force and moment of the axially loaded component 1 in the radial direction are balanced.

[0082] Specifically, in response to the problem that the existing single flywheel cannot balance the radial force and torque on the steering shaft at the same time, in this embodiment, a double balancing weight design is adopted to adjust the first moving component 3 and / or the second moving component 4 to achieve the balance of force and torque in the radial direction of the axial force-bearing component 1, thereby solving the problem that a single balancing weight is difficult to balance the radial force and torque on the rotating shaft at the same time, thereby reducing the vibration and noise caused by the imbalance of radial torque and improving the overall operation stability.

[0083] As a preferred embodiment, the first moving component 3 is a first flywheel, the first flywheel has a first eccentric mass, and the center of mass C of the first flywheel is spaced from the center of mass of the axial force bearing component 1 by a first center of mass eccentricity;

[0084] The second moving component 4 is a second flywheel, the second flywheel has a second eccentric mass, and the center of mass D of the second flywheel is spaced from the center of mass of the axial force bearing component 1 by a second center of mass eccentricity;

[0085] The first eccentric mass and the second eccentric mass are the same or different, and the first center of mass eccentricity and the second center of mass eccentricity are different.

[0086] As a preferred embodiment, the first moving component 3 and the second moving component 4 are located on both sides of the eccentric component 2 .

[0087] As a preferred embodiment, the first moving component 3 and the second moving component 4 are integrally formed.

[0088] Furthermore, the first flywheel and the second flywheel can be designed as a separate design or an integrated design. The integrated double flywheel balance weight structure is simpler to assemble, more compact in structure, and has a wider range of applications.

[0089] The present invention further provides a rotary Stirling refrigerator, comprising an axial force bearing component 1, on which an eccentric component 2 and the above-mentioned double balancing weight device are mounted.

[0090] Specifically, in the micro-vibration damping scheme of the rotary Stirling refrigerator, the present invention adopts a balancing weight design based on a double flywheel to replace the traditional balancing weight design based on a single flywheel. The double flywheel balancing weight design of the present invention adopts two flywheels, which are installed on the rotating shaft of the whole machine with an eccentric shaft, and the force and torque balance of the rotating shaft in the radial direction is achieved by adjusting the eccentricity and mass of the center of mass of the two flywheels.

[0091] Compared with the traditional single flywheel balancing weight structure, the double flywheel balancing weight design adopted in the present invention can reduce the vibration and noise generated by the radial moment imbalance of the rotary Stirling refrigerator, and improve the operating stability of the whole equipment.

[0092] The advantages or beneficial effects of adopting the above technical solution are: the present invention adopts a double balancing weight design to adjust the first moving component 3 and / or the second moving component 4 to achieve the balance of force and torque in the radial direction of the axial force-bearing component 1, thereby solving the problem that a single balancing weight is difficult to simultaneously take into account the balance of radial force and torque on the rotating shaft, thereby reducing the vibration and noise caused by the imbalance of radial force and torque, and improving the overall operation stability.

[0093] The above are only preferred embodiments of the present invention, and are not intended to limit the implementation methods and protection scope of the present invention. Those skilled in the art should be aware that all solutions obtained by equivalent substitutions and obvious changes made using the contents of this specification and illustrations should be included in the protection scope of the present invention.

Claims

1. A vibration reduction method with double balancing weights, characterized in that: include: Step S1, providing an axial force bearing component, wherein an eccentric component is installed on the axial force bearing component; Step S2, installing a first moving component and a second moving component on the axial force bearing component, wherein the eccentric forces of the first moving component, the second moving component and the eccentric component acting on the axial force bearing component are not coplanar; Step S3, adjusting the first moving component and / or the second moving component to balance the force and moment of the axial force-bearing component in the radial direction.

2. The vibration reduction method of double balancing weights according to claim 1, characterized in that: In the step S3, the eccentric mass and the eccentricity of the center of mass of the first moving component and / or the second moving component are adjusted to balance the force and moment of the axial force-bearing component in the radial direction.

3. The vibration reduction method of double balancing weights according to claim 1, characterized in that: The first moving component is a first flywheel, the first flywheel has a first eccentric mass, and the center of mass of the first flywheel is spaced from the center of mass of the axial force bearing component by a first center of mass eccentricity; The second moving component is a second flywheel, the second flywheel has a second eccentric mass, and the center of mass of the second flywheel is spaced from the center of mass of the axial force bearing component by a second center of mass eccentricity; The first eccentric mass and the second eccentric mass are the same or different, and the first center of mass eccentricity and the second center of mass eccentricity are different.

4. The vibration reduction method of double balancing weights according to claim 1, characterized in that: The first moving member and the second moving member are located at both sides of the eccentric member.

5. The vibration reduction method of double balancing weights according to claim 1, characterized in that: The first moving component and the second moving component are integrally formed.

6. A double-balanced counterweight device, comprising an axial force-bearing member, on which an eccentric member is mounted, characterized in that: The device also includes: A first moving component is installed on the axial force bearing component; The second moving component is installed on the axial force-bearing component, wherein the eccentric forces of the first moving component, the second moving component and the eccentric component acting on the axial force-bearing component are not coplanar, and the force and moment of the axial force-bearing component in the radial direction are balanced.

7. The double-balanced counterweight device according to claim 6, characterized in that: The first moving component is a first flywheel, the first flywheel has a first eccentric mass, and the center of mass of the first flywheel is spaced from the center of mass of the axial force bearing component by a first center of mass eccentricity; The second moving component is a second flywheel, the second flywheel has a second eccentric mass, and the center of mass of the second flywheel is spaced from the center of mass of the axial force bearing component by a second center of mass eccentricity; The first eccentric mass and the second eccentric mass are the same or different, and the first center of mass eccentricity and the second center of mass eccentricity are different.

8. The double-balanced counterweight device according to claim 6, characterized in that: The first moving member and the second moving member are located at both sides of the eccentric member.

9. The double-balanced counterweight device according to claim 6, characterized in that: The first moving component and the second moving component are integrally formed.

10. A rotary Stirling refrigerator, characterized in that: It comprises an axial force-bearing component, on which an eccentric component and a double-balanced counterweight device as described in any one of claims 6 to 9 are installed.

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