Variable diameter spring for compressor discharge pipe

Abstract

The utility model discloses a variable diameter spring for compressor exhaust pipe relates to compressor technical field, including first end portion spring and second end portion spring of head -to -tail connection, and the middle section spring of head -to -tail connection is equipped with several sections between two, one end of middle section spring is equipped with first conical spring, and the other end is equipped with second conical spring, and the taper angle of first conical spring and the taper angle of second conical spring are all less than 15 DEG. Realized the clearance fit and the close fit of exhaust pipe. Not only guarantee the exhaust smoothness of exhaust pipe in the working process, also effectively avoided the noise problem produced because of spring hunting.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, specifically to a variable diameter spring for compressor exhaust pipe. Background Technology

[0002] When a refrigerator compressor is working, the piston compresses the refrigerant to produce high-temperature, high-pressure gas, which is then discharged through the internal exhaust pipe into the refrigeration cycle system. The internal exhaust pipe connects the cylinder to the external system, but the periodic impact force generated by the piston or rotor movement can cause the internal exhaust pipe to vibrate, producing noise, leading to fatigue damage or even breakage, affecting the operation of other components and reducing the compressor's lifespan. To solve the vibration problem, damping springs can be added, which absorb vibration energy through elastic deformation and generate a reaction force to reduce vibration. However, the damping springs are loosely fitted to the internal exhaust pipe, making them prone to shifting or falling off during production, transportation, and operation, affecting performance.

[0003] Chinese Patent Publication No. CN205371423U, Publication Date: July 6, 2016, discloses a Chinese patent entitled: A Cross Torsion Spring, comprising a hollow cylindrical helical spring body, wherein the spring body comprises two nested and superimposed first and second units; there is a gap between adjacent helical coils of the first unit, and one end of the first unit is welded with an arc-shaped first torsion arm along the helical winding direction of the first unit, and the other end is welded with an arc-shaped second torsion arm in the opposite direction to the first torsion arm; there is a gap between adjacent helical coils of the second unit, and one end of the second unit is welded with an arc-shaped third torsion arm along the helical winding direction of the second unit on the same side as the first torsion arm, and the other end is welded with an arc-shaped fourth torsion arm in the opposite direction to the third torsion arm on the same side as the second torsion arm; if this spring is used on an exhaust pipe, it is easy to cause surging problems during compressor operation. Utility Model Content

[0004] This utility model provides a variable diameter spring for compressor exhaust pipe. By setting a first conical spring and a second conical spring, it can simultaneously have a clearance fit and a tight fit with the exhaust pipe, ensuring smooth exhaust while avoiding noise caused by surging.

[0005] A further objective of this invention is to reduce the vibration of the exhaust pipe and protect it.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: a variable diameter spring for a compressor exhaust pipe, comprising a first end spring and a second end spring connected end to end, and a plurality of middle springs connected end to end between the two; one end of the middle spring is provided with a first conical spring, and the other end is provided with a second conical spring, the cone angle of the first conical spring and the cone angle of the second conical spring are both less than 15°.

[0007] Preferably, the middle section spring is a helical spring with equal spacing between the first and second conical springs. This ensures uniform force distribution on the spring, improves overall stability, and enhances vibration damping.

[0008] Preferably, the inner end of the first end spring is provided with a second conical spring, and the inner end of the second end spring is provided with a first conical spring. This optimized structure allows for a tighter fit between the spring and the exhaust pipe, improving sealing and vibration damping performance.

[0009] Preferably, the second conical spring at the first end is connected to the first conical spring of the adjacent middle section spring. This enhances the overall spring structure and improves the operational stability of the compressor.

[0010] Preferably, the middle sections of several spring segments are connected by a first conical spring and a second conical spring.

[0011] Preferably, the taper of the first conical spring is 1° to 10°, and the taper of the second conical spring is 2° to 15°. The taper angle of the first conical spring is smaller than that of the second conical spring. This precise taper design ensures smooth exhaust from the exhaust pipe while avoiding noise caused by surging.

[0012] Preferably, the first conical spring of the second end spring is connected to the second conical spring of the adjacent middle section spring.

[0013] Preferably, the first end spring, several middle spring segments, and the second end spring are integrally formed, with the length ratio of adjacent springs being 0.1 to 10. Several middle spring segments are added to the first and second end springs, stacked sequentially until the spring length reaches the preset effect. This improves the overall strength and reliability of the spring, simplifies the assembly process, and reduces production costs.

[0014] Preferably, the ratio of the maximum to the minimum diameter of the variable-diameter spring is 1 to 2. This gradual change in diameter achieves a stiffness gradient transition. Elastic deformation absorbs the vibration energy of the internal exhaust pipe, significantly reducing the vibration amplitude during compressor operation. This stiffness gradient transition ensures the spring can effectively absorb vibration energy under different loads, improving vibration damping performance.

[0015] Preferably, the central axes of the first end spring, several middle-section springs, and the second end spring are on a straight line or on different straight lines. Preferably, they are arranged on a straight line. Through axial nesting and radial limiting design between the springs at each stage, axial movement or radial detachment of the springs during operation is effectively prevented, ensuring long-term operational reliability. This ensures stable operation of the springs during operation, preventing movement or detachment, and guaranteeing long-term reliable operation of the compressor.

[0016] The beneficial effects of this invention are as follows: By setting a first conical spring and a second conical spring, this invention achieves both clearance and tight fit in the exhaust pipe. This design not only ensures smooth exhaust during operation but also effectively avoids noise problems caused by spring movement, significantly improving the quietness of compressor operation.

[0017] This invention reduces exhaust pipe vibration, thereby minimizing the impact and wear on the exhaust pipe and its connecting components. This vibration reduction helps protect the exhaust pipe, extending its service life, and also helps protect other related components of the compressor, improving the stability and reliability of the entire compressor system. Attached Figure Description

[0018] Figure 1 This is a cross-sectional view of the present invention.

[0019] Figure 2 This is an assembly drawing of the present invention.

[0020] Reference numerals in the attached figures: 1: First end spring; 2: Second end spring; 3: Middle section spring; 4: First conical spring; 5: Second conical spring; 6: Exhaust pipe. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0022] When a refrigerator compressor is working, the high-temperature, high-pressure gas formed by the piston compressing the refrigerant is discharged from the high-pressure chamber through the internal exhaust pipe and finally enters the refrigerator's refrigeration cycle system. The internal exhaust pipe is a crucial component connecting the compressor cylinder to the external system. Because the piston or rotor movement inside the compressor generates periodic impact forces, these forces are transmitted through the cylinder to the exhaust pipe system, causing vibration in the internal exhaust pipe. This vibration not only causes noise problems, but long-term vibration can also lead to fatigue damage to the pipe and connecting components, and may even induce fatigue fracture at the connection points. Furthermore, in the high-temperature, high-pressure operating environment, the vibration of the internal exhaust pipe affects the operation of other compressor components, accelerating wear and significantly reducing the compressor's lifespan. Therefore, to solve the vibration problem of the internal exhaust pipe, damping springs are currently added to absorb and mitigate vibration energy. The internal exhaust pipe damping spring in a refrigerator is an energy storage element. It mainly absorbs the vibration energy of the internal exhaust pipe through elastic deformation. When subjected to external vibration, the damping spring undergoes elastic deformation, generating a reaction force to reduce external vibration and ultimately achieve the purpose of vibration reduction.

[0023] Currently, the damping spring and the internal exhaust pipe are fitted with a clearance. Therefore, vibrations generated during the compressor's production and transportation can cause the damping spring on the exhaust pipe to shift or even fall off, which significantly affects the compressor's performance. This invention, a variable-diameter spring for the compressor exhaust pipe, effectively solves these problems through a unique structural design.

[0024] like Figure 1 As shown, the variable diameter spring for the compressor exhaust pipe of this utility model has an ingenious and scientifically designed overall structure. The spring is composed of multiple parts working together, including a first end spring 1 and a second end spring 2 connected end to end. Between these two, there are also several middle section springs 3 connected end to end. These different spring parts cooperate with each other to form a fully functional whole.

[0025] like Figure 1As shown, the middle spring 3, as the core component of the spring structure, has particularly crucial design at both ends. A first conical spring 4 at one end and a second conical spring 5 at the other end form a unique variable-diameter structure. The cone angle design of the first and second conical springs 4 and 5 reflects a deep consideration of practical usage requirements; both cone angles are less than 15°, preferably less than 10°. Furthermore, the cone angle of the first conical spring 4 is smaller than that of the second conical spring 5. This difference in cone angle allows for different degrees of contact and constraint when the springs engage with the exhaust pipe 6. The first conical spring 4, with its relatively gentle taper, forms a moderate clearance fit with the exhaust pipe 6. During compressor operation, this clearance fit provides a smooth passage for exhaust from the exhaust pipe 6, without obstructing the exhaust and ensuring rapid, unobstructed gas discharge. The relatively larger cone angle of the second conical spring 5, while ensuring sufficient exhaust space, allows for a tighter fit with the exhaust pipe 6. When the exhaust pipe 6 shows a tendency to move during operation, the second conical spring 5 can effectively limit the range of movement of the exhaust pipe 6 by means of its close fit, thereby avoiding noise caused by movement and ensuring the quiet operation of the compressor.

[0026] The middle section spring 3, located between the first conical spring 4 and the second conical spring 5, employs a helical equidistant spring design, a design of significant importance. The helical equidistant structure ensures that when the spring is under stress, the force is evenly transmitted and distributed along the helical direction. Regardless of the direction or intensity of vibration generated by the compressor during operation, the helical equidistant spring can evenly distribute these forces throughout the entire spring structure, preventing excessive localized stress that could lead to spring deformation or damage. This uniform force distribution improves the overall stability of the spring, allowing it to maintain good performance over long-term use. Simultaneously, the uniform force distribution also enhances the spring's vibration damping effect. When the exhaust pipe 6 transmits vibrations generated by the compressor to the spring, the helical equidistant spring can more effectively absorb and buffer this vibrational energy, reducing the transmission of vibration to other components, thereby protecting the exhaust pipe 6 and extending its service life.

[0027] In the end structure design of the springs, a second conical spring 5 is provided on the inner end of the first end spring 1, and a first conical spring 4 is provided on the inner end of the second end spring 2. This asymmetrical but complementary structural design further optimizes the fit between the spring and the exhaust pipe 6. The conical spring design at the ends allows the spring to better conform to the shape of the exhaust pipe 6 when connected to the end of the exhaust pipe 6, achieving a tighter fit. This tight fit not only improves the connection stability between the spring and the exhaust pipe 6 but also enhances the constraint effect of the spring on the exhaust pipe 6. During compressor operation, the conical springs at the ends can more effectively limit the vibration and surging of the exhaust pipe 6, further improving vibration damping performance and ensuring that the exhaust pipe 6 can work stably under complex operating conditions.

[0028] The second conical spring 5 of the first end spring 1 is connected to the first conical spring 4 of the adjacent middle section spring 3. Several middle section springs 3 are also connected to each other through the first conical spring 4 and the second conical spring 5. This connection method greatly enhances the overall integrity of the springs. The various springs are connected by conical springs to form a continuous and unified structural system. During compressor operation, when the springs are subjected to external forces, this integrity allows the force to be transmitted quickly and evenly between the various parts of the springs, avoiding local stress concentration or loosening of connections. The various springs work together to cope with the vibration and surging from the exhaust pipe 6, improving the stability of compressor operation and ensuring the reliable operation of the compressor equipment.

[0029] This utility model discloses a variable-diameter spring for the compressor exhaust pipe 6. Through the unique arrangement of the first conical spring 4 and the second conical spring 5, as well as the reasonable design and mutual cooperation of the middle section spring 3 and the end springs, it achieves both clearance fit and tight fit with the exhaust pipe 6. While ensuring smooth exhaust from the exhaust pipe 6, it effectively avoids noise generation, reduces vibration of the exhaust pipe 6, and provides good protection for the exhaust pipe 6. Its structural design is scientific and reasonable, with clear functions for each part and mutual cooperation, which has important practical value and broad application prospects in the field of compressor equipment.

[0030] The tapered design of the first conical spring 4 and the second conical spring 5 is the core element for achieving the ideal fit between the exhaust pipe 6 and the exhaust pipe 6. The taper of the first conical spring 4 is precisely set between 3° and 7°, while the taper of the second conical spring 5 is controlled between 6° and 11°. These two seemingly minor angular parameters have actually undergone extensive mechanical analysis and experimental verification. The smaller taper of the first conical spring 4 creates a just-right gap when assembled with the exhaust pipe 6. This gap is not arbitrarily determined but is carefully considered in relation to the exhaust requirements of the exhaust pipe 6. When the compressor is working, gas is discharged from the exhaust pipe 6, and the gap fit of the first conical spring 4 will not obstruct the airflow, ensuring that the gas can pass smoothly with minimal resistance and maintain the efficient operation of the exhaust system. At the same time, this gap is not too large, so that the exhaust pipe 6 is still constrained by the spring to a certain extent during normal operation, preventing excessive shaking.

[0031] The relatively larger taper of the second conical spring 5 allows for a closer contact with the exhaust pipe 6 while ensuring sufficient exhaust space. When the exhaust pipe 6 tends to swerve due to vibrations from the compressor or airflow impact, the second conical spring 5, with its conical structure, can apply a gradually increasing restraining force to the exhaust pipe 6. This restraint is not rigid; rather, as the swerving amplitude increases, the spring deformation and force increase linearly, effectively suppressing the swerving of the exhaust pipe 6 and preventing noise caused by metal-to-metal collisions. The differentiated taper design of the two conical springs acts like a precise regulator, achieving a perfect balance between smooth exhaust and noise reduction.

[0032] The connection method of each part of the spring is also carefully designed. The first conical spring 4 of the second end spring 2 is connected to the second conical spring 5 of the adjacent middle section spring 3. This connection method makes the transition between the spring sections natural and the connection tight. During the operation of the spring, when it is subjected to external force transmitted by the exhaust pipe 6, the force can be transmitted quickly and evenly along the connection parts of the conical springs, avoiding the risk of local damage caused by stress concentration at the connection point. The spring sections are connected by the nested conical structure to form a continuous force-bearing whole. Whether it is the absorption of vibration energy or the constraint effect on the exhaust pipe 6, they can all work together in the overall structure of the spring, further enhancing the working performance of the spring.

[0033] The first end spring 1, several middle-section springs 3, and the second end spring 2 are manufactured using a one-piece molding process, which offers multiple advantages. One-piece molding avoids the weak points that may arise from traditional segmented manufacturing and reassembly, significantly improving the overall strength of the spring. During manufacturing, precise control of mold parameters ensures that the length ratio of adjacent springs is within the range of 0.1-10. This length ratio design is not arbitrary but based on considerations of the spring's stress characteristics and actual working requirements. Shorter spring segments can deform quickly under stress, absorbing high-frequency vibration energy; longer spring segments can handle low-frequency, large-amplitude vibrations, buffering larger external impacts through their elastic deformation. By rationally setting the length ratio of each spring segment, the spring can absorb and buffer the vibration transmitted by the exhaust pipe 6 in a comprehensive and multi-layered manner under different working conditions.

[0034] Meanwhile, several intermediate spring segments 3 are added between the first end spring 1 and the second end spring 2, and are stacked sequentially until the spring length reaches the preset effect. This modular design allows the spring to be flexibly adjusted according to different models and operating requirements of the compressor exhaust pipe 6. For scenarios requiring longer springs to enhance vibration damping, simply increase the number of intermediate spring segments 3; for installation environments with limited space, the number of spring segments can be appropriately reduced to meet installation requirements while ensuring performance. The one-piece molding process not only improves the overall strength and reliability of the spring but also simplifies the assembly process. Compared to traditional multi-part assembled springs, one-piece molded springs eliminate the need for complex assembly procedures, reducing manual operation and time costs, while also reducing the risk of quality problems caused by improper assembly, further lowering production costs.

[0035] The ratio of the maximum to the minimum diameter of the variable-diameter spring is controlled between 1 and 2, a parameter setting that achieves a gradient transition in spring stiffness. The change in spring diameter is not simply a difference in size, but is closely related to stiffness characteristics. As the spring diameter gradually changes from minimum to maximum, its stiffness also forms a gradient distribution from large to small. During compressor operation, when the exhaust pipe 6 is subjected to small vibrations or external forces, the smaller diameter end of the spring (with higher stiffness) can respond quickly, providing sufficient support and suppressing minor lateral movement of the exhaust pipe 6. When the vibration amplitude increases or the external force intensifies, the larger diameter end of the spring (with lower stiffness) takes effect, absorbing more vibration energy through greater elastic deformation. This gradient stiffness design allows the spring to adaptively adjust its stress and deformation state according to different load conditions, effectively absorbing vibration energy under various operating conditions, significantly reducing the vibration amplitude during compressor operation, and improving the spring's vibration damping performance.

[0036] The central axes of the first end spring 1, several middle-section springs 3, and the second end spring 2 are kept on the same straight line, which is an important design feature to ensure stable operation of the springs. Through the axial nesting and radial limiting design between the various spring stages, the possibility of axial movement or radial detachment of the springs during operation is structurally eliminated. In the axial direction, the conical structures of adjacent spring segments nest together, forming a constraint relationship similar to a tenon and mortise joint. When the spring is subjected to axial force, each spring segment can tightly engage to resist external force and prevent axial displacement. In the radial direction, the helical structure of the spring and its fit with the exhaust pipe 6 naturally limit the radial movement of the spring. Even under extreme conditions, such as sudden severe vibration of the compressor, the spring can maintain stable operation in its predetermined working position thanks to this dual axial and radial limiting design, avoiding performance failure or safety hazards caused by spring displacement, and providing a solid guarantee for the long-term reliable operation of the compressor.

[0037] In summary, this utility model's variable diameter spring for compressor exhaust pipes achieves a perfect balance between clearance and tight fit through innovation and optimization in various aspects, including the spring's taper, connection method, manufacturing process, diameter variation, and shaft design. This not only ensures smooth exhaust flow and eliminates operating noise but also effectively protects the exhaust pipe and other compressor components through superior vibration damping performance. This comprehensive performance improvement significantly enhances the stability and reliability of the compressor system, demonstrating significant practical value and broad application prospects in the industrial equipment field.

[0038] Obviously, the above embodiments are merely illustrative examples for clear explanation and are not intended to limit the implementation. Those skilled in the art will recognize that other variations or modifications can be made based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations here. However, obvious variations or modifications derived therefrom are still within the protection scope of this utility model.

Claims

1. A variable diameter spring for a compressor exhaust pipe, characterized in that, It includes a first end spring and a second end spring connected end to end, with several middle springs connected end to end between them. The middle section spring has a first conical spring at one end and a second conical spring at the other end. The cone angle of the first conical spring and the cone angle of the second conical spring are both less than 15°.

2. The variable diameter spring for a compressor exhaust pipe according to claim 1, characterized in that, The middle section spring is a helical equidistant spring located between the first and second conical springs.

3. A variable diameter spring for a compressor exhaust pipe according to claim 1, characterized in that, The inner end of the first end spring is provided with a second conical spring, and the inner end of the second end spring is provided with a first conical spring.

4. A variable diameter spring for a compressor exhaust pipe according to claim 3, characterized in that, The second conical spring at the first end is connected to the first conical spring of the adjacent middle section spring.

5. A variable diameter spring for a compressor exhaust pipe according to claim 1, 2, or 3, characterized in that, The first and second conical springs are connected to each other among several middle sections of the spring.

6. A variable diameter spring for a compressor exhaust pipe according to claim 1, 2, or 3, characterized in that, The taper of the first conical spring is 1° to 10°, and the taper of the second conical spring is 2° to 15°.

7. A variable diameter spring for a compressor exhaust pipe according to claim 3, characterized in that, The first conical spring at the second end is connected to the second conical spring of the adjacent middle section spring.

8. A variable diameter spring for a compressor exhaust pipe according to claim 1, characterized in that, The first end spring, several middle section springs, and the second end spring are integrally formed, and the length ratio of adjacent springs is 0.1 to 10.

9. A variable diameter spring for a compressor exhaust pipe according to claim 8, characterized in that, The ratio of the maximum diameter to the minimum diameter inside a variable diameter spring is 1 to 2.

10. A variable diameter spring for a compressor exhaust pipe according to claim 1 or 8, characterized in that, The central axes of the first end spring, several middle section springs, and the second end spring are on the same straight line or on different straight lines.

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