Low-vibration high-limit pressure scroll machine and design method thereof

Abstract

The application belongs to the field of scroll machines, and particularly relates to a low-vibration high-limit-pressure scroll machine and a design method thereof. The scroll machine comprises a first cavity, a dynamic scroll tooth and a static scroll tooth arranged in the first cavity, and a stability device arranged in a second cavity connected with the first cavity. The stability device comprises a mass block and a plurality of elastic damping mechanisms. An end surface of the mass block is connected with the dynamic scroll tooth, and a circumferential surface of the mass block is connected with the plurality of elastic damping mechanisms. The elastic damping mechanisms are used for reducing vibration when the dynamic scroll tooth rotates. The scroll machine and the design method thereof can significantly reduce vibration of the scroll machine and improve the limit pressure of the scroll machine. When the scroll machine vibrates under the action of the eccentric mass, the elastic damping mechanisms can avoid rapid displacement of the mass block, thereby realizing the function of reducing vibration.

Description

Technical Field

[0001] This invention belongs to the field of scroll machines, specifically relating to a low-vibration, high-ultimate-pressure scroll machine and its design method. Background Technology

[0002] Scroll compressors and expanders are widely used in refrigeration, pressurization, and other fields due to their high efficiency and reliability. The efficient operation of scroll compressors relies on the periodic decrease in volume and increase in pressure created by the rotating moving scroll and stationary scroll. The blades of the moving scroll move in close contact with the outer wall of the stationary scroll. During this periodic change in pressure and volume, especially at low speeds, the scroll exhibits significant vibration characteristics, primarily caused by the alternating dynamic and static friction forces. This leads to large fluctuations in pressure within the enclosed space formed by the moving and stationary scrolls, reducing the scroll compressor's ultimate operating pressure. Furthermore, the movement of the liquid within the enclosed space formed by the moving and stationary scroll blades causes periodic changes in the center of gravity, further increasing the scroll compressor's vibration. To address these issues, this invention, based on mechanical vibration theory, provides a scroll compressor and design scheme that can adapt to all operating conditions with low vibration amplitude and high ultimate pressure, effectively reducing vibration and cavity pressure fluctuations while increasing the scroll compressor's ultimate operating pressure. Summary of the Invention

[0003] The purpose of this invention is to provide a low-vibration, high-ultimate-pressure scroll mill and its design method to solve the problems existing in the prior art. To achieve the above-mentioned objective, the technical solution adopted by this invention is as follows:

[0004] A low-vibration, high-ultimate-pressure scroll mill includes a first cavity containing a moving scroll tooth and a stationary scroll tooth, and a stabilization device disposed in a second cavity connected to the first cavity. The stabilization device includes an intermediate mass and multiple elastic damping mechanisms. The end face of the intermediate mass is connected to the moving scroll tooth, and the circumferential surface of the intermediate mass is connected to the multiple elastic damping mechanisms. The elastic damping mechanisms are used to reduce the vibration of the moving scroll tooth during rotation.

[0005] Furthermore, the elastic damping mechanism includes a damper and an elastic component, with the two ends of the damper and the elastic component respectively connected to the second cavity and the intermediate mass component.

[0006] Furthermore, the damping of the damper, the stiffness of the elastic component, the mass of the intermediate mass component, and the maximum design speed of the vortex machine satisfy the following formula:

[0007]

[0008] In the formula, k sM represents the stiffness of an elastic component. s ω represents the mass of the intermediate mass component. s The maximum design speed of the vortex turbine is represented by μ. s This indicates the damping value of the damper.

[0009] Furthermore, a receiving cavity is provided in the second cavity, and the elastic damping mechanism and the intermediate mass are located in the receiving cavity. The two ends of the damper and the elastic component are respectively fixedly connected to the inner wall surface of the receiving cavity and the intermediate mass.

[0010] Furthermore, the top of the second cavity is connected to the bottom of the first cavity, and the bottom of the second cavity is connected to a drive connection part for driving the second cavity to rotate. The moving vortex tooth is disposed on the bottom surface of the first cavity, and the stationary vortex tooth is fixedly disposed relatively statically.

[0011] Furthermore, six elastic damping mechanisms are provided, evenly distributed around the rotation center of the intermediate mass component.

[0012] A design method for a low-vibration, high-ultimate-pressure vortex machine includes:

[0013] With the goal of minimizing vibration amplitude, and based on the maximum design speed of the vortex machine, the relationship between the damping of the damper, the stiffness of the elastic component, and the mass of the intermediate mass component is obtained by formula.

[0014] An installation design method for a low-vibration, high-ultimate-pressure scroll mill includes:

[0015] Determine the locations of the theoretical center of mass, actual center of mass, and liquid outlet point of the vortex turbine, and design them to lie on the same straight line, satisfying the following formula:

[0016] l4 = l3 - l1 (6)

[0017] Where l3 is the distance between the liquid output point and the theoretical centroid, l4 is the distance between the liquid output point and the actual centroid, and l1 is the distance between the theoretical centroid and the actual centroid.

[0018] When installing a vortex machine, the mass of the vortex machine is adjusted to minimize the value of l1, thus compensating for the distance between the theoretical and actual centers of mass.

[0019] Furthermore, when compensating for the distance between the theoretical and actual centroids, the following formula is satisfied:

[0020]

[0021] Where K0 represents the moment of inertia of the scroll machine, M0 represents the mass of the scroll machine, and l2 represents the straight-line distance from the center of rotation of the scroll machine to the actual center of mass of the scroll machine.

[0022] Furthermore, the mass of the scroll machine is adjusted by changing the mass of the intermediate mass component, and the total mass of the first cavity, the moving scroll tooth, and the stationary scroll tooth is equal to the mass of the intermediate mass component.

[0023] The present invention has the following beneficial effects: The vortex machine and its design method provided by the present invention can significantly reduce the vibration of the vortex machine and increase the ultimate pressure of the vortex machine. By setting multiple elastic damping mechanisms around the intermediate mass component, when the vortex machine vibrates under the action of the eccentric mass, the elastic damping mechanisms can prevent the intermediate mass component from rapidly displacing, thereby achieving the function of stability. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the elastic damping mechanism.

[0025] Figure 2 This is a schematic diagram showing the distribution relationship between the first and second cavities;

[0026] Figure 3 A schematic diagram of the structure of the moving and stationary vortex gears;

[0027] Figure 4 This is a schematic diagram showing the location of the centroid.

[0028] Figure 5 A simplified schematic diagram showing the distance relationship between the center of mass, the center of rotation, and the liquid output point. Detailed Implementation

[0029] The following will refer to the appendices in the embodiments of the present invention. Figures 1-5 The technical solutions in the embodiments of the present invention will be clearly and completely described. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Unless otherwise specified, the technical means used in the embodiments are conventional means well known to those skilled in the art.

[0030] In the description of this invention, it should be understood that the terms "longitudinal", "lateral", "up", "down", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0031] like Figure 1 , Figure 2A low-vibration, high-ultimate-pressure scroll mill includes a first cavity containing a moving scroll tooth and a stationary scroll tooth, and a stabilization device disposed in a second cavity connected to the first cavity. The stabilization device includes an intermediate mass 4 and multiple elastic damping mechanisms. The end face of the intermediate mass 4 is connected to the moving scroll tooth, and the circumferential surface of the intermediate mass 4 is connected to the multiple elastic damping mechanisms. The elastic damping mechanisms are used to reduce the vibration of the moving scroll tooth during rotation.

[0032] Specifically, by setting an intermediate mass component 4, the mass distribution of the scroll mill is balanced, ensuring that the overall center of mass, i.e., the center of gravity, of the scroll mill is located at the center of rotation. During the rotation of the moving scroll gear, the intermediate mass component 4 rotates together, and the resulting eccentric motion is absorbed by the elastic damping mechanism, reducing the eccentric displacement of the intermediate mass component 4 and the moving scroll gear. This weakens the vibration of the intermediate mass component 4 and the moving scroll gear, ultimately improving the performance of the scroll mill, such as its ultimate pressure and ultimate speed.

[0033] Furthermore, the elastic damping mechanism includes a damper 2 and an elastic component 3, with the two ends of the damper 2 and the elastic component 3 respectively connected to the second cavity and the intermediate mass component 4.

[0034] Specifically, the elastic component 3 is preferably a spring, and specifically a spring made of a negative Poisson's ratio material. The damper 2 is preferably a viscoelastic damper, and its damping value is equal to the damping value of the material of the cavity 2.

[0035] Furthermore, the damping of the damper 2, the stiffness of the elastic component 3, the mass of the intermediate mass component 4, and the maximum design speed of the vortex machine satisfy the following formula:

[0036]

[0037] In the formula, k s M represents the stiffness of an elastic component. s ω represents the mass of the intermediate mass component. s The maximum design speed of the vortex turbine is represented by μ. s This represents the damping value of the damper. This formula is derived based on the principle of mechanical vibration. By measuring the vibration amplitude of the vortex machine through experimental methods, the above formula (5) can be obtained when the vibration amplitude meets the design target and is minimized. Therefore, in this invention, as long as the stiffness of the elastic component, the mass of the intermediate mass component, and the damping of the damper are matched according to this formula, the vibration can be minimized.

[0038] By employing the damper 2 and elastic component 3 with the above characteristics, the stability of the scroll mill can be guaranteed under any operating condition when the actual operating speed is less than or equal to the maximum design speed. This ensures the balance between the eccentric force generated by the eccentric mass and the eccentric force generated by the intermediate mass component 4. For example, if the maximum design speed is 2000 r / min, then using the spring stiffness obtained from the above formula will allow the scroll mill to maintain stability even when the actual operating speed is below 2000 r / min.

[0039] Furthermore, a receiving cavity 1 is provided in the second cavity, and the elastic damping mechanism and the intermediate mass 4 are located in the receiving cavity 1. The two ends of the damper 2 and the elastic component 3 are respectively fixedly connected to the inner wall surface of the receiving cavity 1 and the intermediate mass 4.

[0040] Specifically, six elastic damping mechanisms are evenly distributed around the rotation center of the intermediate mass 4, forming a hexagonal structure with the accommodating cavity 1 and the intermediate mass 4. Each side is equipped with a corresponding elastic damping mechanism. Choosing six elastic damping mechanisms and the intermediate mass 4 to form a stability system satisfies the requirement of reducing dynamic imbalance, reduces cost and installation / adjustment difficulty, improves installation stability, and ensures stable and reliable operation. If there are fewer than six elastic damping mechanisms, the stability will be difficult to meet the predetermined requirements. If there are more than six elastic damping mechanisms, although the requirements can be met, the installation / adjustment difficulty and cost increase significantly, without a significant improvement in performance. Furthermore, the displacement direction of the elastic component 3 and the damping direction of the damper 2 are both perpendicular to the side of the corresponding intermediate mass 4.

[0041] Furthermore, the top of the second cavity is connected to the bottom of the first cavity, and the bottom of the second cavity is connected to a drive connection part for driving the second cavity to rotate. The moving vortex tooth is disposed on the bottom surface of the first cavity, and the stationary vortex tooth is fixedly disposed in a relatively static manner. Preferably, the stationary vortex tooth is fixedly connected to the top surface of the first cavity, and the top surface of the first cavity is connected to other fixed parts of the vortex machine. The fixed parts may be bracket-type structures. The top surface of the first cavity is rotatably connected to the first cavity and forms a sealed structure.

[0042] Specifically, the drive connection part is based on existing technology, connecting corresponding rotating components such as motors. On the horizontal plane, the intermediate mass 4 and the moving vortex gear are movable. The moving vortex gear is detachably mounted in the first cavity via grooved fasteners, and a counterweight washer is provided inside the moving vortex gear. The center of gravity of the vortex machine can be adjusted by replacing counterweight washers of different thicknesses and weights. The counterweight washer and the moving vortex gear are fixed using recessed screws.

[0043] The top of the second cavity is detachably fitted with a cover plate that seals the accommodating cavity 1, and the intermediate mass 4 is movably located within the second cavity. When the second cavity rotates, the first cavity and the moving vortex gear rotate together, and the intermediate mass 4 rotates as well. The eccentric displacement generated by the vortex machine is absorbed by an elastic damping mechanism. Under the action of the damping mechanism, the intermediate mass 4 absorbs vibration energy, reduces vibration, and achieves a stable function.

[0044] This invention also relates to a design method for a low-vibration, high-ultimate-pressure scroll mill, comprising:

[0045] With the goal of minimizing vibration amplitude, and based on the maximum design speed of the vortex turbine, the relationship between the damping of damper 2, the stiffness of elastic component 3, and the mass of intermediate mass component 4 is obtained as Equation 5. When designing the damping of damper 2, the stiffness of elastic component 3, and the mass of intermediate mass component 4, the corresponding specific values ​​can be calculated based on Equation 5 under the minimum vibration amplitude of the vortex turbine.

[0046] The scroll mill and its design method provided by this invention can significantly reduce the vibration of the scroll mill and increase its ultimate pressure. An intermediate mass 4 is installed in the second cavity so that the overall center of mass of the scroll mill is located on its rotation axis. Multiple elastic damping mechanisms are arranged around the intermediate mass 4. When the scroll mill vibrates under the action of the eccentric mass, the dampers 2 of the multiple elastic damping mechanisms pre-tighten the intermediate mass 4. The elastic components 3 prevent the intermediate mass 4 from rapidly displacing. The dampers 2 further reduce the displacement of the intermediate mass 4 and absorb energy when the elastic components 3 recover their deformation, creating a phase difference and a certain degree of hysteresis. Under the action of the eccentric mass, the elastic components 3 cause the intermediate mass 4 to displace in the opposite direction to the eccentric mass, meaning the eccentric mass, the intermediate mass 4, and the rotation center are on a straight line, thus achieving stability. The combination of the intermediate mass 4 and the multiple elastic damping mechanisms can reduce the impact of imbalance caused by manufacturing and installation errors of the scroll mill, reduce the fluctuation of the output pressure during the operation of the scroll mill, thereby reducing vibration and increasing the ultimate pressure.

[0047] like Figure 3During the movement of the moving and stationary vortex teeth, three variable volumes are periodically formed. The pressure of the liquid within each variable volume gradually increases with the movement of the moving and stationary vortex teeth. The outlet is where the liquid is discharged as the relative movement of the moving and stationary vortex teeth reduces the volume due to the increased pressure within the variable volume, thus increasing the liquid pressure. The volumes of the three variable volumes can be obtained using either the finite element method or the integral method. The finite element method involves establishing the volumes of the moving and stationary vortex teeth and the first cavity, which are obtained through Boolean operations in the software. The integral method involves first integrating the involute functions of the moving and stationary vortex teeth in the plane, and then integrating along the height of the vortex teeth. During the actual machining and installation of the moving and stationary vortex teeth, the bottom surface, and other components, errors inevitably occur, causing the center of mass of the entire assembled component to be off-axis. The inconsistent pressure in each variable volume exacerbates this center-of-mass shift.

[0048] Therefore, it is necessary to compensate for the distance between the theoretical centroid and the actual centroid. For example... Figure 4 , Figure 5 The present invention also relates to an installation design method for a low-vibration, high-ultimate-pressure scroll mill, comprising:

[0049] The first step is to determine the locations of the theoretical center of mass, the actual center of mass, and the liquid output point of the vortex turbine, and design these three points to be on the same straight line, satisfying the following formula:

[0050] l4 = l3 - l1 (6)

[0051] Where l3 is the distance between the liquid output point and the theoretical centroid, l4 is the distance between the liquid output point and the actual centroid, and l1 is the distance between the theoretical centroid and the actual centroid.

[0052] The second step is to adjust the mass of the vortex machine during installation, with the minimum value of l1 as the target, to compensate for the distance between the theoretical center of mass and the actual center of mass.

[0053] In the second step, when compensating for the distance between the theoretical and actual centroids, the following formula is satisfied:

[0054]

[0055] Where K0 represents the moment of inertia of the scroll machine, M0 represents the mass of the scroll machine, and l2 represents the straight-line distance from the center of rotation of the scroll machine to the actual center of mass of the scroll machine.

[0056] In the second step, the mass of the vortex machine can be adjusted by changing the mass of the intermediate mass component 4. The total mass of the first cavity, the moving vortex tooth, and the stationary vortex tooth is equal to the mass of the intermediate mass component 4, which can balance the eccentric force generated by the eccentric mass of the vortex machine with the eccentric force generated by the intermediate mass component 4, and quickly reduce vibration.

[0057] In addition, the moment of inertia, mass, actual center of mass position, and theoretical center of mass position can be determined through experimental measurements. The liquid output point, which is the liquid outlet within the scroll turbine, is determined by measuring the liquid output position within the assembled scroll turbine.

[0058] During the operation of the scroll compressor, since the liquid output point is the pressure center, the installation positions of the moving and stationary scroll teeth, as well as the first and second cavities, ensure that the pressure or impact on the moving scroll teeth during operation will not cause any normal reaction force to the rotation center of the moving scroll teeth. This improves the working stability of the moving scroll teeth, reduces the vibration caused by the periodic pressurization and depressurization of the moving scroll teeth, and increases the ultimate pressure of the scroll teeth.

[0059] The installation design method of the scroll mill of the present invention takes into account the error of the center of mass deviation during the installation of the scroll mill. By adjusting the mass of the scroll mill and changing the distribution of the center of mass, this error is compensated and the additional vibration caused by the error can be eliminated. During the high-speed rotation of the scroll mill, since the moving scroll teeth apply pressure to the liquid, the output liquid has a reaction force on the scroll mill that is equal in magnitude and opposite in direction to this pressure. The direction of the force on the scroll mill that balances the tangential component of the moving scroll teeth is not on the same straight line as the rotation center of the scroll mill, thereby avoiding the impact of the periodic pressure fluctuations during the high-speed rotation of the scroll mill on the rotation center of the scroll mill.

[0060] In addition, in this invention, "center of mass" refers to the position of the center of gravity of the component.

[0061] The embodiments described above are merely preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Any modifications, alterations, substitutions, or variations made by those skilled in the art to the technical solutions of the present invention without departing from the spirit of the present invention shall fall within the protection scope defined by the claims of the present invention.

Claims

1. A low-vibration high-limit pressure scroll machine comprising a first cavity in which a orbiting scroll and a fixed scroll are disposed, characterized by: It also includes a stabilization device, which is disposed in a second cavity connected to the first cavity. The stabilization device includes an intermediate mass (4) and multiple elastic damping mechanisms. The end face of the intermediate mass (4) is connected to the moving vortex tooth, and the circumferential surface of the intermediate mass (4) is connected to multiple elastic damping mechanisms. The elastic damping mechanisms are used to reduce the vibration when the moving vortex tooth rotates. The installation design method for low-vibration, high-ultimate-pressure scroll compressors is as follows: Determine the locations of the theoretical center of mass, actual center of mass, and liquid outlet point of the vortex turbine, and design them to lie on the same straight line, satisfying the following formula: （6） in The distance between the liquid output point and the theoretical centroid. The distance between the liquid output point and the actual centroid is . This represents the distance between the theoretical center of mass and the actual center of mass. When installing a vortex machine, with The goal is to minimize the mass of the vortex turbine and compensate for the distance between the theoretical and actual centers of mass.

2. The low-vibration, high-ultimate-pressure scroll mill according to claim 1, characterized in that: The elastic damping mechanism includes a damper (2) and an elastic component (3), with the two ends of the damper (2) and the elastic component (3) respectively connected to the second cavity and the intermediate mass component (4).

3. The low-vibration, high-ultimate-pressure scroll mill according to claim 2, characterized in that: The damping of the damper (2), the stiffness of the elastic component (3), the mass of the intermediate mass component (4), and the maximum design speed of the vortex machine satisfy the following formula: （5） In the formula, Indicates the stiffness of the elastic component (3), This indicates the mass of the intermediate mass component (4). This indicates the maximum design speed of the scroll engine. This indicates the damping value of the damper (2).

4. A low-vibration, high-ultimate-pressure scroll mill according to claim 2, characterized in that: The second cavity is provided with a receiving cavity (1), the elastic damping mechanism and the intermediate mass (4) are located in the receiving cavity (1), and the two ends of the damper (2) and the elastic component (3) are respectively fixedly connected to the inner wall surface of the receiving cavity (1) and the intermediate mass (4).

5. A low-vibration, high-ultimate-pressure scroll mill according to claim 1, characterized in that: The top of the second cavity is connected to the bottom of the first cavity, and the bottom of the second cavity is connected to a drive connection part for driving the second cavity to rotate. The moving vortex tooth is disposed on the bottom surface of the first cavity, and the stationary vortex tooth is fixedly disposed with relative stillness.

6. A low-vibration, high-ultimate-pressure scroll mill according to any one of claims 1-5, characterized in that: The elastic damping mechanism is provided in six parts, which are evenly distributed around the rotation center of the intermediate mass (4).

7. A low-vibration, high-ultimate-pressure scroll mill according to claim 1, characterized in that: When compensating for the distance between the theoretical and actual centroids, the following formula is satisfied: （7） in This represents the moment of inertia of the scroll engine. This indicates the mass of the scroll engine. This represents the straight-line distance from the rotation center of the scroll machine to its actual center of mass.

8. A low-vibration, high-ultimate-pressure scroll mill according to claim 7, characterized in that: The mass of the vortex machine is adjusted by changing the mass of the intermediate mass component (4). The total mass of the first cavity, the moving vortex tooth, and the stationary vortex tooth is equal to the mass of the intermediate mass component (4).

9. A design method for a low-vibration, high-ultimate-pressure scroll mill, applied to the low-vibration, high-ultimate-pressure scroll mill of claim 3, characterized in that: include: With the goal of minimizing vibration amplitude, and based on the maximum design speed of the vortex turbine, the relationship between the damping of the damper (2), the stiffness of the elastic component (3), and the mass of the intermediate mass component (4) is obtained as follows: （5） In the formula, Indicates the stiffness of the elastic component (3), This indicates the mass of the intermediate mass component (4). This indicates the maximum design speed of the scroll engine. This indicates the damping value of the damper (2).

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