Exhaust non-return structure and compressor

Abstract

The application discloses an exhaust check structure and a compressor. The exhaust check structure comprises a static vortex disc, a compression cavity, an exhaust groove and an exhaust passage. The exhaust groove is communicated with the compression cavity and the exhaust passage. The exhaust passage is transversely arranged in the static vortex disc and communicated with the side wall of the static vortex disc. A first valve is arranged in the exhaust passage. A positioning passage is arranged in the vertical direction of the static vortex disc and communicated with the exhaust passage. A second valve is arranged in the positioning passage. The second valve is abutted with the first valve to block the exhaust passage. The two valves are cooperated with relative sliding by the motion principle. The stability of the exhaust check structure is improved. The noise problem during the operation of the compressor is effectively solved. Meanwhile, the relative sliding motion mode reduces the violent impact of the valve and enhances the reliability of the exhaust check structure.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to an exhaust check structure and a compressor. Background Art

[0002] In air conditioning systems, the compressor is a core component, and its performance plays a decisive role in the air conditioner's energy efficiency. Scroll compressors, a type of positive displacement compressor, are widely used in the air conditioning field due to their high efficiency, energy saving, and stable operation.

[0003] The operating principle of a scroll compressor is that a motor drives the crankshaft to rotate, which in turn drives the orbiting scroll to orbit and translate around the stationary scroll. This motion creates a periodic change in the enclosed volume, ultimately compressing the gas. However, during compressor operation, there is a pressing issue: when the pressure on the discharge side exceeds the pressure within the scroll chamber, refrigerant backflow occurs, causing the compressor to reverse. This reverse rotation not only generates considerable noise but also seriously affects compressor reliability.

[0004] To increase the exhaust area, existing scroll compressors typically feature an irregularly shaped exhaust port, and the accompanying exhaust check valve is a thin, circular disc. During compressor operation, the high-pressure gas discharged from the exhaust port exerts a significant force, and this force is not perpendicular to the valve's center of mass, leading to a series of problems.

[0005] On the one hand, the strength and rigidity of the valve disc face severe challenges. As the valve disc moves downward, it rapidly impacts the gasket stop. Since only the edge of the valve disc interacts with the gasket, the immense impact force can easily cause the disc to deform or even break. This not only significantly shortens the service life of the exhaust check valve disc but also has a serious negative impact on the reliability of the compressor.

[0006] Furthermore, the stability of the valve disc's movement is difficult to guarantee. Due to the irregular shape of the exhaust slot, the exhaust airflow is eccentric relative to the exhaust check valve disc. The force of the airflow causes the thin disc to tip and deflect significantly during its ascent, exacerbating friction with the restraining surface of the valve seat and generating annoying noise.

[0007] In summary, existing high-speed scroll compressor exhaust check structures have significant deficiencies in valve plate strength, rigidity, and motion stability, failing to meet practical application requirements. Therefore, designing a high-speed scroll compressor exhaust check structure that can avoid severe impact during operation while also providing excellent reliability and motion stability has become a pressing technical challenge in the field. Summary of the Invention

[0008] The purpose of the present invention is to overcome the deficiencies of the prior art and to provide an exhaust check structure and a compressor.

[0009] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0010] In the first aspect, an embodiment of the present invention provides an exhaust check structure, comprising: a static scroll, the static scroll being provided with a compression chamber, an exhaust groove and an exhaust channel, the exhaust groove being connected to the compression chamber and the exhaust channel, the exhaust channel being laterally arranged inside the static scroll and connected to the side wall of the static scroll, a first valve member being provided in the exhaust channel, a positioning channel being further provided in the vertical direction of the static scroll, and the positioning channel being connected to the exhaust channel, a second valve member being provided in the positioning channel, the second valve member being in contact with the first valve member to form a blockage for the exhaust channel.

[0011] In a specific embodiment, the exhaust channel includes a small end and a large end, the inner diameter of the large end is larger than the small end, the small end is connected to the exhaust groove, the first valve component is arranged at the large end, and the outer diameter of the first valve component is larger than the inner diameter of the small end.

[0012] In a specific embodiment, the large end portion is further provided with a spring, one end of the spring abuts against the end surface of the large end portion, and the other end of the spring abuts against the first valve member.

[0013] In a specific embodiment, the first valve member is provided with a first inclined surface at one end away from the spring, and the second valve member is provided with a second inclined surface at one end close to the first valve member. The second inclined surface and the first inclined surface are matched to form a blockage for the exhaust passage.

[0014] In a specific embodiment, the sum of the bevel angle of the first bevel and the bevel angle of the second bevel is 90 degrees.

[0015] In a specific embodiment, the first inclined surface has an angle of 30-60 degrees.

[0016] In a specific embodiment, the positioning channel intersects the axis of the exhaust channel at right angles, and the inner diameter of the positioning channel is equal to the inner diameter of the large end portion.

[0017] In a specific embodiment, the second valve member is provided with an open groove along the length direction, and a limit block is provided on the upper surface of the static scroll, and the limit block is adapted to the open groove.

[0018] In a specific embodiment, the limit stopper is a cuboid, and the width of the limit stopper is equal to the width of the opening slot.

[0019] The exhaust check structure of the present invention has the following advantages over the prior art: by utilizing the principle of motion, the reciprocating motion of a single valve disc in the prior art structure is converted into the relative sliding motion of two valve members (a first valve member and a second valve member). This relative sliding motion makes the moving parts more stable during operation, avoids large-scale shaking and deviation of the valve disc due to eccentric airflow, effectively improves the stability of the moving parts in the exhaust check structure during movement, and provides reliable protection for the stable operation of the compressor. In addition, the relative sliding motion of the two valve members makes the exhaust process smoother, significantly reduces the noise generated by airflow impact and friction, effectively solves the noise problem during compressor operation, and improves the user comfort of the product. In addition, the two valve members abut against each other, and can better disperse and withstand the applied force during movement. Compared with the prior art method of a single valve disc bearing impact, this design achieves more uniform stress distribution and reduces the risk of damage to the valve members due to localized excessive force. At the same time, the relative sliding motion reduces severe impact on the valve members, further extending the service life of the valve members, effectively enhancing the reliability of the exhaust check structure, and improving the overall performance and service life of the compressor.

[0020] In a second aspect, an embodiment of the present invention provides a compressor comprising the exhaust check structure as described above.

[0021] The compressor of the present invention has the following advantages over the prior art: by providing an exhaust check structure and utilizing the principle of motion, the reciprocating motion of a single valve disc in the prior art structure is converted into the relative sliding motion of two valve members (a first valve member and a second valve member). This relative sliding motion makes the moving parts more stable during operation, avoids large-scale shaking and deviation of the valve disc due to eccentric airflow, effectively improves the stability of the moving parts in the exhaust check structure during movement, and provides reliable protection for the stable operation of the compressor. In addition, the relative sliding motion of the two valve members makes the exhaust process smoother, significantly reduces the noise generated by airflow impact and friction, effectively solves the noise problem during compressor operation, and improves the user comfort of the product. In addition, the two valve members abut against each other, and can better disperse and withstand the applied force during movement. Compared with the prior art method of a single valve disc bearing impact, this design makes the stress distribution more uniform and reduces the risk of damage to the valve member due to local excessive force. At the same time, the relative sliding motion reduces the severe impact of the valve member, further extending the service life of the valve member, effectively enhancing the reliability of the exhaust check structure, and improving the overall performance and service life of the compressor.

[0022] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0024] Figure 1 A schematic front view of the exhaust check structure provided by the present invention;

[0025] Figure 2 A schematic cross-sectional view of the exhaust check structure provided by the present invention;

[0026] Figure 3 An exploded schematic diagram of the exhaust check structure provided by the present invention;

[0027] Figure 4 A schematic structural diagram of a first valve member provided by the present invention;

[0028] Figure 5 A schematic structural diagram of a second valve member provided by the present invention;

[0029] Reference numerals:

[0030] The fixed scroll 10 , the compression chamber 11 , the exhaust groove 12 , the exhaust channel 13 , the positioning channel 14 , the first valve member 20 , the first inclined surface 21 , the second valve member 30 , the second inclined surface 31 , the opening groove 32 , the spring 40 , and the limit block 50 . DETAILED DESCRIPTION

[0031] In order to make the objectives, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0032] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. 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 those skilled in the art without creative work shall fall within the scope of protection of the present invention.

[0033] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0034] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature identified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined.

[0035] In the present invention, unless otherwise expressly specified or limited, terms such as "mounted," "connected," "connect," and "fixed" should be understood broadly. For example, these terms may refer to connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of these terms in the present invention based on specific circumstances.

[0036] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Furthermore, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0037] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms should not be understood as necessarily referring to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification.

[0038] See also Figures 1 to 5 As shown, the present invention discloses a specific embodiment of an exhaust check structure, including: a static scroll 10, the static scroll 10 is provided with a compression chamber 11, an exhaust groove 12 and an exhaust channel 13, the exhaust groove 12 is connected to the compression chamber 11 and the exhaust channel 13, the exhaust channel 13 is transversely arranged inside the static scroll 10 and connected to the side wall of the static scroll 10, a first valve member 20 is provided in the exhaust channel 13, a positioning channel 14 is further provided in the vertical direction of the static scroll 10, and the positioning channel 14 is connected to the exhaust channel 13, a second valve member 30 is provided in the positioning channel 14, the second valve member 30 abuts against the first valve member 20 to form a blockage of the exhaust channel 13.

[0039] Specifically, the static scroll 10 is first precision-machined, and a compression chamber 11, an exhaust groove 12, an exhaust channel 13 and a positioning channel 14 are machined inside the static scroll 10 according to the design requirements. Among them, the compression chamber 11 is used to compress the gas, and the exhaust groove 12 serves to connect the compression chamber 11 and the exhaust channel 13, so that the compressed gas can smoothly enter the exhaust channel 13. The exhaust channel 13 is arranged horizontally inside the static scroll 10, and one end is connected to the side wall of the static scroll 10 to discharge the compressed gas into the system outside the compressor. The positioning channel 14 is machined along the vertical direction of the static scroll 10 and is connected to the exhaust channel 13 to provide space for the installation and movement of the second valve component 30. In addition, after the machining of the static scroll 10 is completed, the first valve component 20 is installed in the exhaust channel 13. The shape and size of the first valve component 20 must be compatible with the exhaust passage 13 to ensure that it can move smoothly in the exhaust passage 13. Then, the second valve component 30 is installed in the positioning passage 14, and the position of the second valve component 30 is adjusted so that it abuts against the first valve component 20. Through this abutment relationship, the two valve components form a whole and jointly realize the blocking and opening control of the exhaust passage 13.

[0040] When the compressor is operating normally, the gas in the compression chamber 11 is compressed and the pressure gradually increases. When the pressure in the compression chamber 11 reaches a certain level, the gas enters the exhaust channel 13 through the exhaust groove 12. At this time, the gas exerts an outward force on the first valve member 20, trying to push the first valve member 20 outward to open the exhaust channel 13 so that the compressed gas can be discharged. Because the second valve member 30 is in contact with the first valve member 20 and the second valve member 30 is restricted by the positioning channel 14, under the action of gas pressure, relative slippage occurs between the first valve member 20 and the second valve member 30. This relative slippage causes the first valve member 20 to gradually move outward and the second valve member 30 to gradually move upward, so that the first valve member 20 and the second valve member 30 no longer completely overlap, and the first valve member 20 is connected, that is, the exhaust channel 13 is opened, and the compressed gas can be discharged smoothly. When exhaust is completed, the second valve member 30 resets under the action of its own gravity and drives the first valve member 20 back to its initial position. At this time, the second valve member 30 abuts against the first valve member 20, so that the first valve member 20 is closed, that is, the exhaust passage 13 is re-blocked to prevent external gas from flowing back into the compression chamber 11, thereby realizing a non-return function.

[0041] Specifically, in the prior art, exhaust check structures typically utilize a single valve disc that performs reciprocating motion to achieve both exhaust and check functions. This reciprocating motion makes the valve disc susceptible to uneven airflow distribution during movement, resulting in tilting, wobbling, and other phenomena, resulting in poor motion stability. However, the exhaust check structure utilizes the principles of motion to transform the reciprocating motion of the single valve disc in the prior art structure into the relative sliding motion of two valve components (first valve component 20 and second valve component 30). This relative sliding motion ensures smoother operation of the moving components, preventing significant wobbling and displacement of the valve disc due to eccentric airflow. This effectively improves the stability of the moving components in the exhaust check structure and provides reliable assurance for the stable operation of the compressor. Furthermore, the unstable valve disc motion in the prior art can lead to severe collision and friction between the valve disc and components such as the valve seat, resulting in high exhaust noise. This noise not only affects the operating environment of the compressor but can also negatively impact its performance. This exhaust check structure improves the stability of moving parts and reduces collisions and friction between the valve and related components. The relative sliding movement of the two valves makes the exhaust process smoother, significantly reducing the noise generated by airflow impact and friction, effectively solving the noise problem during compressor operation and improving the user comfort of the product. In addition, in the prior art, the valve plate needs to withstand large impact and friction during reciprocating motion, which can easily cause the valve plate to wear, deform, or even break, thereby affecting the reliability and service life of the exhaust check structure. In this exhaust check structure, the two valves abut against each other to better disperse and withstand the applied force during movement. Compared with the prior art method of a single valve plate bearing impact, this design makes the stress distribution more uniform and reduces the risk of damage to the valve due to excessive local force. At the same time, the relative sliding movement reduces the severe impact of the valve, further extending the service life of the valve, effectively enhancing the reliability of the exhaust check structure and improving the overall performance and service life of the compressor.

[0042] See also Figure 2 As shown, in one embodiment, the exhaust channel 13 includes a small end and a large end, the inner diameter of the large end is larger than that of the small end, the small end is connected to the exhaust groove 12, the first valve member 20 is arranged at the large end, and the outer diameter of the first valve member 20 is larger than the inner diameter of the small end.

[0043] Specifically, the exhaust passage 13 is a through hole formed inside the fixed scroll 10 and connects the exhaust groove 12 to the circumferential sidewall of the fixed scroll 10. The first valve member 20 is disposed at the large end, and its outer diameter is larger than the inner diameter of the small end to prevent the first valve member 20 from sliding into the small end.

[0044] More specifically, the position and direction of the exhaust channel 13 in the static scroll 10 are first determined according to the design requirements. The exhaust channel 13 is a through hole opened inside the static scroll 10, one end of which is connected to the exhaust groove 12, and the other end is connected to the circumferential side wall of the static scroll 10, so as to realize the path of compressed gas being discharged from the compression chamber 11 through the exhaust groove 12 and the exhaust channel 13 to the external system of the compressor. When processing the exhaust channel 13, it is designed to be a structure including a small end and a large end. The small end is precisely connected to the exhaust groove 12 to ensure that the compressed gas can smoothly enter the exhaust channel 13 from the exhaust groove 12. The inner diameter of the large end is larger than the inner diameter of the small end, forming a stepped channel structure. In addition, the material of the first valve component 20 needs to have good wear resistance and corrosion resistance to adapt to the working environment inside the compressor. The outer diameter of the first valve member 20 is precisely machined based on the inner diameter of the larger end portion, ensuring that it is larger than the inner diameter of the smaller end portion. Furthermore, the first valve member 20 can be smoothly inserted into the larger end portion with an appropriate clearance between it and the inner wall of the larger end portion, ensuring that the first valve member 20 can move flexibly within the larger end portion. When installing the first valve member 20, slowly insert it through the opening of the larger end portion to ensure accurate positioning. Because the outer diameter of the first valve member 20 is larger than the inner diameter of the smaller end portion, the first valve member 20 is confined within the larger end portion and prevents it from sliding into the smaller end portion, thereby ensuring its correct position and proper operation within the exhaust passage 13.

[0045] That is, during compressor operation, the gas pressure within the exhaust passage 13 fluctuates continuously. When the gas within the compression chamber 11 is compressed and enters the exhaust passage 13, it exerts an outward force on the first valve member 20, attempting to push the first valve member 20 outward and the second valve member 30 upward, thereby opening the exhaust passage 13 and allowing the gas to escape. If the first valve member 20 slips into the small end, the exhaust passage 13 will not open properly, preventing the compressed gas from being discharged smoothly. This will affect the compressor's compression efficiency and may even cause excessive internal pressure in the compressor, leading to a malfunction. The design of the first valve member 20 with an outer diameter larger than the inner diameter of the small end effectively prevents the first valve member 20 from slipping into the small end, ensuring that the first valve member 20 always moves within the large end. When exhaust is required, the first valve member 20 can move outward normally under the action of gas pressure, while the second valve member 30 moves upward, opening the exhaust passage 13. If gas backflow occurs, the second valve member 30 drops, driving the first valve member 20 inward to reset, blocking the exhaust passage 13. This ensures the proper function of the exhaust check structure and improves the operational reliability of the compressor. In addition, the small end and the large end of the exhaust channel 13 are designed to form a gradually expanding structure. When the compressed gas enters the exhaust channel 13 from the exhaust groove 12, it first passes through the small end. Since the inner diameter of the small end is smaller, the gas flow rate is faster, and the gas can be quickly introduced into the exhaust channel 13. The gas then enters the large end. The inner diameter of the large end is larger, the gas flow rate is relatively slow, and the pressure distribution is more uniform. This gradually expanding structure helps to reduce the turbulence and eddy current of the gas in the exhaust channel 13, reduces the resistance to gas flow, and thus reduces energy loss. Compared with the traditional equal-diameter exhaust channel 13, it can make the compressed gas discharged more smoothly, improve the energy efficiency ratio of the compressor, and reduce energy consumption.

[0046] See also Figure 2 As shown, in one embodiment, the large end portion is further provided with a spring 40 , one end of the spring 40 abuts against the end surface of the large end portion, and the other end abuts against the first valve member 20 .

[0047] Specifically, the outer diameter of spring 40 is larger than the inner diameter of the smaller end portion, and one end of spring 40 abuts the end surface of the larger end portion, preventing the first valve member 20 from sliding into the smaller end portion and acting as a position limiter. In the initial state, under the force of spring 40, the first valve member 20 and the second valve member 30 are tightly fitted together, completely overlapping and sealing the exhaust passage 13.

[0048] More specifically, the appropriate type and specifications of spring 40 are selected based on factors such as the operating pressure of the exhaust check structure, the mass of the first valve member 20, and the required spring force. For example, if a higher spring force is required to ensure that the first valve member 20 tightly seals the exhaust passage 13 in its initial state, while also ensuring that the spring 40 maintains good elasticity and durability during frequent compression and extension, a compression spring can be selected. Materials such as stainless steel with high strength and corrosion resistance can be used. Furthermore, the outer diameter of the spring 40 should be larger than the inner diameter of the small end. This prevents the first valve member 20 from accidentally sliding into the small end during compression and extension, ensuring that the first valve member 20 always moves within the large end. Furthermore, the free length and compressed length of the spring 40 should be precisely determined based on the depth of the large end and the travel of the first valve member 20 to ensure that the spring 40 provides the appropriate preload after installation.

[0049] In other words, the design of spring 40 with an outer diameter larger than the inner diameter of the smaller end, combined with the design of first valve member 20 with an outer diameter larger than the inner diameter of the smaller end, creates a dual position-limiting mechanism. During compressor operation, when gas pressure changes cause the first valve member 20 to slide toward the smaller end, spring 40 not only prevents movement of the first valve member 20 through its own elastic force, but its larger outer diameter also physically blocks the first valve member 20 from sliding into the smaller end. This dual position-limiting mechanism significantly improves the stability of the exhaust check structure, avoiding the problem of failure to seal the exhaust passage 13 due to misalignment of the first valve member 20, and ensuring the normal operation of the compressor. In addition, in the initial state, the force of spring 40 causes the first valve member 20 and the second valve member 30 to fit tightly together and completely overlap, effectively sealing the exhaust passage 13. Spring 40 provides a stable preload that can be precisely adjusted according to the actual operating requirements of the compressor. Compared to structures without spring 40, exhaust check structures with spring 40 are more adaptable to varying operating pressures and operating conditions. In the initial stage of compressor startup or when pressure fluctuation is small, the preload force of the spring 40 is sufficient to ensure a tight fit between the first valve member 20 and the second valve member 30 to prevent gas leakage.

[0050] See also Figures 2 to 5 As shown, in one embodiment, the first valve member 20 is provided with a first inclined surface 21 at one end away from the spring 40, and the second valve member 30 is provided with a second inclined surface 31 at one end close to the first valve member 20, and the second inclined surface 31 and the first inclined surface 21 are matched to form a blockage for the exhaust passage 13.

[0051] Specifically, the first valve member 20 is a hollow cylindrical slider with a gas passageway. The second valve member 30 is a solid or hollow cylindrical slider with an end cap on top, preventing gas from escaping through the second valve member 30. In the initial state, under the force of the spring 40, the horizontal first inclined surface 21 and the vertical second inclined surface 31 are tightly aligned, with the two inclined surfaces completely overlapping. The passageway within the first valve member 20 is completely blocked by the second valve member 30, preventing external air from entering the compression chamber 11.

[0052] More specifically, a suitable metal material, such as stainless steel, is selected to ensure that the valve member has sufficient strength, wear resistance, and corrosion resistance. A first bevel 21 is machined on the end of the first valve member 20 away from the spring 40. Similarly, a suitable material, such as stainless steel, is machined into a hollow cylindrical slider, namely the second valve member 30. Furthermore, a second bevel 31 is machined on the end of the second valve member 30 closer to the first valve member 20 using a milling process similar to that used to machine the first bevel 21. During the machining process, the angle and dimensions of the second bevel 31 must be strictly matched to those of the first bevel 21, ensuring that the second bevel 31 completely overlaps with the first bevel 21 to achieve a good sealing effect.

[0053] In other words, the mating design of the first bevel 21 and the second bevel 31 forms a line-contact seal. Compared to traditional flat seals, line-contact seals can generate greater sealing pressure over a smaller contact area, thereby better preventing gas from leaking through the gap between the valve components. In the initial state, the force of the spring 40 tightly seals the two bevels, further enhancing the sealing effect. When the internal pressure of the compressor fluctuates, this sealing structure effectively maintains the blockage of the exhaust passage 13, preventing compressed gas from flowing back or external gas from entering the compression chamber 11, thereby improving the operating efficiency and performance stability of the compressor. Furthermore, both the first valve component 20 and the second valve component 30 are hollow cylindrical sliders. This design ensures that when the two bevels mate to seal the exhaust passage 13, the second valve component 30 completely seals the passage within the first valve component 20. This dual sealing mechanism significantly improves sealing reliability, reduces the possibility of gas leakage, and ensures the normal operation of the compressor under various operating conditions. Furthermore, the mating of the first and second bevels 21 and 31, as well as the design of the hollow cylindrical slider, ensures the structural stability of the entire exhaust check structure. During the operation of the compressor, even if affected by external factors such as large pressure fluctuations and vibrations, the two valve components can maintain a relatively stable position through the fit of the inclined surfaces and the force of the spring 40, ensuring the normal sealing and opening of the exhaust passage 13.

[0054] In one embodiment, the sum of the bevel angles of the first bevel 21 and the second bevel 31 is 90 degrees.

[0055] Specifically, based on parameters such as the compressor's operating pressure range, exhaust flow rate, and valve material properties, theoretical calculations were conducted using knowledge of fluid mechanics and mechanical mechanics to determine the appropriate angle combination for the first and second bevels 21, 31 while still meeting sealing and motion requirements. For example, by simulating the gas pressure, spring force, and friction experienced by the valve at different angles, and analyzing the valve's motion and sealing performance, the angle of the first bevel 21 was determined to be α, and the angle of the second bevel 31 to be 90 degrees minus α, so that the sum of the two angles was 90 degrees.

[0056] That is to say, when the sum of the angles of the first bevel 21 and the second bevel 31 is 90 degrees, the two bevels can completely overlap to form a line contact seal. Compared with traditional surface contact seals, this sealing method can generate greater sealing pressure on a smaller contact area. During the operation of the compressor, even if the internal pressure is high, the line contact seal can effectively prevent the gas from leaking through the gap between the valve parts, greatly improving the sealing performance of the exhaust channel 13, reducing the energy loss of the compressed gas, and improving the working efficiency of the compressor. In addition, since the angle design of the two bevels allows them to fit tightly, when the valve part is slightly deformed due to factors such as gas pressure and temperature changes, the line contact seal can automatically adjust the contact state to maintain a good sealing effect. This adaptive sealing feature enables the exhaust check structure to operate stably under various complex working conditions, thereby improving the reliability and stability of the compressor. In addition, the angle combination of the first bevel 21 and the second bevel 31 provides a precise guiding effect for the movement of the valve part. Under the action of gas pressure, the first valve member 20 moves outward and the second valve member 30 moves upward. The first inclined surface 21 and the second inclined surface 31 slide relative to each other, making the valve members move more smoothly and accurately, and preventing deviation and shaking during movement. The guiding effect of the inclined surfaces ensures more uniform contact and friction between the valve members, reducing local stress concentration. Furthermore, this smooth movement reduces collisions and impacts between the valve members, reducing noise generated during exhaust, and improving the compressor's operating environment.

[0057] In one embodiment, the first inclined surface 21 has an angle of 30-60 degrees.

[0058] Specifically, the first bevel 21 forms an angle with the horizontal plane along the length of the first valve member 20. When the angle of the first bevel 21 is between 30 and 60 degrees, it creates a more reasonable contact pressure distribution when in contact with the second bevel 31. A smaller angle (e.g., 30 degrees) allows for a longer contact surface. Under the action of the spring force, the pressure is more evenly distributed across the contact surface, enhancing the sealing effect and preventing gas leakage. A larger angle (e.g., 60 degrees) can also generate sufficient sealing pressure under a certain spring force and gas pressure, ensuring that gas does not leak through the valve member gap under high-pressure conditions. Under low-pressure conditions, a smaller angle of the first bevel 21 makes the valve member easier to open and close while maintaining good sealing performance. Because gas pressure is lower at low pressures, a smaller angle ensures that the valve member responds quickly under the action of the spring force, achieving switching between sealing and opening. Under high-pressure conditions, a larger angle of the first bevel 21 can withstand greater gas pressure, preventing the valve member from being dislodged by high-pressure gas and ensuring a reliable seal.

[0059] See also Figure 2 As shown, in one embodiment, the positioning channel 14 intersects the axis of the exhaust channel 13 at right angles, and the inner diameter of the positioning channel 14 is equal to the inner diameter of the large end portion.

[0060] Specifically, the design of the positioning channel 14 intersecting perpendicularly with the axis of the exhaust channel 13 provides precise guidance for the valve member. When the second valve member 30 slides within the positioning channel 14, it can precisely move in a direction perpendicular to the axis of the exhaust channel 13, preventing deviation or wobbling of the second valve member 30 during movement and improving the movement accuracy of the second valve member 30. Furthermore, the inner diameter of the positioning channel 14 is equal to the inner diameter of the large end portion, ensuring stable support for the second valve member 30 within the positioning channel 14. Furthermore, because the positioning channel 14 intersects perpendicularly with the axis of the exhaust channel 13 and offers high dimensional accuracy, in its initial state, the second valve member 30 fits tightly against the first valve member 20, blocking the exhaust channel 13 and preventing external gas from entering the compression chamber 11. When the compressor is discharging gas, the first valve member 20 moves outward, while the second valve member 30 separates from the first valve member 20 and moves upward, allowing gas to be discharged smoothly through the exhaust channel 13. This precise fit effectively prevents gas leakage and improves compressor efficiency.

[0061] See also Figure 1 、 Figure 3 and Figure 5 As shown, in one embodiment, the second valve member 30 is provided with an open groove 32 along the length direction, and the upper surface of the fixed scroll 10 is provided with a limit block 50 , and the limit block 50 is adapted to the open groove 32 .

[0062] Specifically, the stopper 50 is fixed to the upper surface of the fixed scroll 10 by screws. During exhaust, the first valve member 20 is forced outward along the exhaust passage 13 by the force of the exhaust airflow. Because the inclined surfaces of the first and second valve members 20 and 30 are tightly aligned, the second valve member 30 slides relative to the first valve member 20 along the direction of the contact inclined surface under the action of the first valve member 20, i.e., the second valve member 30 moves upward along the positioning passage 14. At this point, the inclined surfaces of the first and second valve members 20 and 30 no longer completely overlap. The passage within the first valve member 20 connects to the exhaust passage 13, and the refrigerant airflow within the compression chamber 11 passes through the exhaust groove 12, the small end, the passage within the first valve member 20, and the large end, ultimately being discharged. As the second valve member 30 moves upward, the stopper 50 also moves relative to the opening groove 32 of the second valve member 30. Ultimately, the stopper 50 contacts the lower end of the opening groove 32, acting as a limiter and terminating the movement of the second valve member 30. At this point, the second valve member 30 still partially contacts the inclined surface of the first valve member 20, acting as a restraint on the first valve member 20 and preventing it from sliding out of the exhaust passage 13. After exhaust is complete, the second valve member 30 returns to its original position under its own weight, driving the first valve member 20 back to its initial position. The first inclined surface 21 and the second inclined surface 31 overlap, closing the internal passage of the first valve member 20 and preventing external gas from flowing back into the compression chamber 11, thus achieving a check function.

[0063] In other words, the coordinated design of the stopper 50 and the opening slot 32 can accurately limit the further movement of the second valve member 30 when it reaches its upper limit, preventing the second valve member 30 from sliding out of the positioning channel 14, thereby avoiding damage to the second valve member 30 and compressor failure. For example, during the compressor exhaust process, if the second valve member 30 does not have a limiting device, it may move upward excessively under the action of the airflow, causing collisions with other components and causing damage to the equipment. The presence of the stopper 50 can effectively prevent this from occurring, ensuring the safety of the movement of the second valve member 30. In addition, the precise design of the opening slot 32 and the stopper 50 ensures that the second valve member 30 moves along a predetermined trajectory during movement, improving the movement accuracy of the second valve member 30. The precise movement trajectory helps to more accurately match the inclined surfaces between the first valve member 20 and the second valve member 30, thereby ensuring the normal implementation of the exhaust and check functions. Furthermore, after exhaust is complete, the second valve member 30 resets under its own weight and drives the first valve member 20 back to its initial position. The first inclined surface 21 and the second inclined surface 31 overlap, closing the internal passage of the first valve member 20. At this point, the second valve member 30 still partially contacts the inclined surfaces of the first valve member 20, allowing the second valve member 30 to restrain the first valve member 20 and prevent it from slipping out of the exhaust passage 13. Furthermore, the second valve member 30 quickly resets under its own weight, driving and sealing the first valve member 20. This rapid response allows the compressor to promptly prevent gas backflow after exhaust is complete, reducing energy loss and compressor operating fluctuations, thereby improving compressor efficiency.

[0064] See also Figure 1 and Figure 3 As shown, in one embodiment, the limit stopper 50 is a rectangular parallelepiped, and the width of the limit stopper 50 is equal to the slot width of the opening slot 32 .

[0065] Specifically, because the width of the stopper 50 is equal to the width of the slot 32, the stopper 50 can be tightly embedded in the slot 32, effectively preventing the second valve member 30 from shaking or shifting during its movement. For example, when the compressor is exhausting, the second valve member 30 will move due to the force of the airflow. If there is a gap between the stopper 50 and the slot 32, the second valve member 30 may experience lateral shaking during movement, affecting the precision of the valve member's fit with the first valve member 20, leading to problems such as poor exhaust or a loose seal. However, precise width matching ensures stable movement of the valve member in the predetermined direction, improving the reliability of the valve member's movement. Furthermore, the precise fit between the stopper 50 and the slot 32 accurately controls the travel of the second valve member 30. When the second valve member 30 moves upward, the limit block 50 slides relatively in the opening groove 32. When the limit block 50 contacts the lower end of the opening groove 32, the movement of the second valve member 30 is terminated, achieving precise limiting. This accurate movement stroke control is crucial to ensuring the normal exhaust and check function of the compressor, and can avoid equipment failure caused by excessive or insufficient movement of the valve member.

[0066] The present invention also discloses a compressor comprising the exhaust check structure described above.

[0067] Specifically, by providing an exhaust check structure and utilizing the principle of motion, the reciprocating motion of a single valve disc in the existing structure is converted into the relative sliding motion of two valve components (first valve component 20 and second valve component 30). This relative sliding motion makes the moving components more stable during operation, avoids large-scale shaking and deviation of the valve disc due to eccentric airflow, effectively improves the stability of the moving components in the exhaust check structure during movement, and provides reliable protection for the stable operation of the compressor. In addition, the relative sliding motion of the two valve components makes the exhaust process smoother, significantly reduces the noise generated by airflow impact and friction, effectively solves the noise problem during compressor operation, and improves the user comfort of the product. In addition, the two valve components abut against each other, and can better disperse and withstand the applied force during movement. Compared with the existing method of a single valve disc bearing impact, this design achieves more uniform stress distribution and reduces the risk of damage to the valve components due to local excessive force. At the same time, the relative sliding motion reduces severe impact on the valve components, further extending the service life of the valve components, effectively enhancing the reliability of the exhaust check structure, and improving the overall performance and service life of the compressor.

[0068] The above embodiments are preferred implementation schemes of the present invention. In addition, the present invention can also be implemented in other ways. Any obvious replacement without departing from the concept of the present technical solution is within the scope of protection of the present invention.

Claims

1. An exhaust check structure, characterized in that: include: A stationary scroll, wherein the stationary scroll is provided with a compression chamber, an exhaust groove, and an exhaust passage, the exhaust groove being connected to the compression chamber and the exhaust passage, the exhaust passage being transversely arranged inside the stationary scroll and connected to a side wall of the stationary scroll, a first valve member being provided in the exhaust passage, a positioning passage being further provided in a vertical direction of the stationary scroll, and the positioning passage being connected to the exhaust passage, a second valve member being provided in the positioning passage, the first valve member being provided with a first inclined surface, and the second valve member being provided with a second inclined surface; the second valve member abutting against the first valve member so that the first inclined surface and the second inclined surface are matched to form a sealing block for the exhaust passage; The exhaust passage includes a small end and a large end, the inner diameter of the large end is larger than that of the small end, the small end is connected to the exhaust groove, the first valve member is arranged at the large end, and the outer diameter of the first valve member is larger than the inner diameter of the small end; the large end is also provided with a spring, one end of the spring abuts against the end surface of the large end, and the other end abuts against the first valve member.

2. The exhaust check structure according to claim 1, characterized in that: The first inclined surface is provided on one end of the first valve member away from the spring, and the second inclined surface is provided on one end of the second valve member closer to the first valve member.

3. The exhaust check structure according to claim 2, characterized in that: The sum of the bevel angle of the first bevel and the bevel angle of the second bevel is 90 degrees.

4. The exhaust check structure according to claim 3, characterized in that: The first inclined surface has an angle of 30-60 degrees.

5. The exhaust check structure according to claim 1, characterized in that: The positioning channel intersects the axis of the exhaust channel at right angles, and the inner diameter of the positioning channel is equal to the inner diameter of the large end portion.

6. The exhaust check structure according to claim 1, characterized in that: The second valve member is provided with an open groove along the length direction, and a limit block is provided on the upper surface of the static scroll, and the limit block is adapted to the open groove.

7. The exhaust check structure according to claim 6, characterized in that: The limit stopper is a cuboid, and the width of the limit stopper is equal to the width of the opening slot.

8. A compressor, characterized in that: It comprises the exhaust check structure according to any one of claims 1 to 7.

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