Exhaust valve assembly for compressor and compressor

Abstract

The invention relates to the technical field of compression equipment, and discloses an exhaust valve assembly for a compressor, which can ensure that a valve plate is triggered in time to release an exhaust port and slow down the springback speed of the valve plate when the operation frequency of the compressor is relatively low. And when the operation frequency of the compressor is relatively high, the valve plate can be prevented from delaying to close the exhaust port, so that the effects of improving the cooling capacity of the refrigeration equipment and reducing the input power are achieved. Meanwhile, the invention further discloses the compressor.

Description

Technical Field

[0001] This application relates to the field of compression equipment technology, for example to an exhaust valve assembly for a compressor and a compressor. Background Technology

[0002] Compressors are a crucial component of refrigeration equipment such as refrigerators and air conditioners, and their performance generally has a decisive impact on the cooling and heating effects of these devices. With the continuous development of compressor technology, users are increasingly demanding higher energy efficiency and full-range operating performance from compressors. As a core component of refrigeration and heating equipment, the compressor's operating efficiency directly affects the overall energy consumption and user experience. During the compressor's operation, the discharge valve assembly is a key structural element, and its performance plays a decisive role in the compressor's COP (Coefficient of Performance), discharge resistance loss, and operational stability.

[0003] In related technologies, compressor exhaust valve assemblies often adopt a reed valve structure, which consists of a bearing valve seat, exhaust valve plate, lift limiter and rivets. The lift limiter limits the maximum lift of the valve plate to ensure the overall reliability of the compressor.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In related technologies, existing exhaust valve assemblies, due to their design characteristics, cannot simultaneously adapt to the compressor's operating requirements at different frequencies. For example, during low-frequency operation, the closing angle may be premature, leading to overcompression of unexhausted gas; while during high-frequency operation, the valve plate may close late, causing high-pressure refrigerant to flow back into the cylinder. These problems not only reduce the cooling capacity of the refrigeration equipment but also further increase the input power due to the secondary compression of the backflowing gas.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides an exhaust valve assembly for a compressor and a compressor. When the compressor operates at a low frequency, it can ensure that the valve plate is triggered in time to release the exhaust port and delay the rebound speed of the valve plate. When the compressor operates at a high frequency, it can prevent the valve plate from delaying the closure of the exhaust port, thereby increasing the cooling capacity of the refrigeration equipment and reducing the input power.

[0009] This disclosure provides an exhaust valve assembly for a compressor, comprising: a valve seat, a valve plate, and a lift limiter. The valve seat has an exhaust port; the valve plate has a first end mounted on the valve seat and a second end covering the exhaust port, the valve plate including a first elastic portion near the first end and a second elastic portion near the second end, the stiffness of the first elastic portion being greater than or equal to a preset stiffness, and the stiffness of the second elastic portion being less than the preset stiffness; the lift limiter is mounted on the valve seat and includes a limiting structure located above the valve plate; wherein the first and second elastic portions of the valve plate are used to bend the valve plate away from the valve seat to release the exhaust port.

[0010] In some embodiments, the first elastic portion and the second elastic portion of the valve plate are configured as an integrally formed structure; the width of the first elastic portion is greater than the width of the second elastic portion.

[0011] In some embodiments, the first end and the second end of the first elastic portion are respectively connected to the first end and the second elastic portion of the valve plate; wherein the width of the second end of the first elastic portion gradually increases from the first end.

[0012] In some embodiments, the second end of the valve plate is configured to be circular, and the diameter of the second end of the valve plate is a first diameter d; the distance from the first end of the first elastic portion to the second end of the valve plate is a first length L, and the distance from the second end of the first elastic portion to the second end of the valve plate is a second length l; wherein, 0.38L+d≤l≤0.6L+d.

[0013] In some embodiments, the limiting structure of the lift limiter includes a first limiting portion and a second limiting portion, wherein the first limiting portion is located on the side of the second limiting portion closer to the valve plate, and the size of the second limiting portion is larger than the size of the first limiting portion.

[0014] In some embodiments, the distance from the first limiting part to the valve plate is a first height h1, and the distance from the second limiting part to the valve plate is a second height h2; wherein, 0.4h2≤h1≤0.75h2.

[0015] In some embodiments, the second height h2 is greater than or equal to 2.5 mm and less than or equal to 4 mm.

[0016] In some embodiments, the first limiting portion is configured as an elastic material; the second limiting portion is configured as a rigid material.

[0017] In some embodiments, the connection between the first end of the valve plate and the first elastic portion is configured with an arc-shaped chamfer structure; the connection between the first elastic portion and the second elastic portion is configured with an arc-shaped chamfer structure.

[0018] This disclosure also provides a compressor comprising: the above-described exhaust valve assembly for a compressor.

[0019] The present disclosure provides an exhaust valve assembly for a compressor and a compressor, which can achieve the following technical effects:

[0020] This disclosure provides an exhaust valve assembly for a compressor, comprising: a valve seat, a valve plate, and a lift limiter. The valve seat has an exhaust port; the valve plate has a first end mounted on the valve seat and a second end covering the exhaust port, the valve plate including a first elastic portion near the first end and a second elastic portion near the second end, the stiffness of the first elastic portion being greater than or equal to a preset stiffness, and the stiffness of the second elastic portion being less than the preset stiffness; the lift limiter is mounted on the valve seat and includes a limiting structure located above the valve plate; wherein the first and second elastic portions of the valve plate are used to bend the valve plate away from the valve seat to release the exhaust port. Thus, when the compressor operates at a low frequency, the exhaust port pressure triggers the second elastic portion but does not trigger the first elastic portion, causing the first elastic portion of the valve plate to remain in its original state while the second elastic portion bends to release the exhaust port; when the compressor operates at a high frequency, the exhaust port pressure simultaneously triggers both the first and second elastic portions, causing both the first and second elastic portions of the valve plate to bend simultaneously to release the exhaust port. Meanwhile, the lift limiter can limit the lifting height of the second end of the valve plate and assist the valve plate in rebounding. This design ensures that the valve plate is triggered promptly to release the exhaust port and slows down the rebound speed when the compressor operates at a low frequency; and prevents the valve plate from delaying the closure of the exhaust port when the compressor operates at a high frequency, thereby increasing the cooling capacity of the refrigeration equipment and reducing input power.

[0021] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0022] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0023] Figure 1 This is a schematic diagram of the structure of an exhaust valve assembly provided in an embodiment of this disclosure;

[0024] Figure 2 This is a cross-sectional view of an exhaust valve assembly provided in an embodiment of this disclosure;

[0025] Figure 3 This is a partial cross-sectional view of an exhaust valve assembly provided in an embodiment of this disclosure;

[0026] Figure 4 This is a schematic diagram of the structure of a valve plate provided in an embodiment of this disclosure;

[0027] Figure 5 This is a schematic diagram of the structure of a lift limiter provided in an embodiment of this disclosure;

[0028] Figure 6 This is a schematic diagram of another lift limiter provided in an embodiment of this disclosure.

[0029] Figure label:

[0030] 10: Valve seat; 11: Exhaust port; 12: Fastener;

[0031] 20: Valve plate; 21: First elastic part; 22: Second elastic part;

[0032] 30: Lift limit switch; 31: First limit part; 32: Second limit part. Detailed Implementation

[0033] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0034] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0035] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0036] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0037] Unless otherwise stated, the term "multiple" means two or more.

[0038] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0039] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0040] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0041] Existing compressors typically use reed valves with a lift limiter to limit the maximum lift of the valve plate. To ensure overall compressor reliability, the valve plate must possess high reliability, meaning it must meet requirements such as impact resistance and high rigidity. During low-frequency operation, the valve plate closes earlier than at higher frequencies, causing overcompression of undischarged gas and increasing compressor input power. However, reducing the valve plate rigidity leads to a longer closing time during high-frequency operation, potentially causing the valve plate to remain open at the end of high-frequency discharge. This results in high-pressure refrigerant flowing back into the cylinder, reducing compressor cooling capacity. Furthermore, the recirculated gas undergoes secondary compression, further increasing compressor input power.

[0042] like Figures 1 to 6 As shown, this disclosure provides an exhaust valve assembly for a compressor and a compressor. When the compressor operates at a low frequency, it can ensure that the valve plate 20 is triggered in time to release the exhaust port 11 and delay the rebound speed of the valve plate 20. When the compressor operates at a high frequency, it can prevent the valve plate 20 from delaying the closing of the exhaust port 11, thereby achieving the effect of increasing the cooling capacity of the refrigeration equipment and reducing the input power.

[0043] like Figures 1 to 6As shown, this disclosure provides an exhaust valve assembly for a compressor, comprising: a valve seat 10, a valve plate 20, and a lift limiter 30. The valve seat 10 has an exhaust port 11; the valve plate 20 has a first end mounted on the valve seat 10 and a second end covering the exhaust port 11. The valve plate 20 includes a first elastic portion 21 near the first end and a second elastic portion 22 near the second end. The stiffness of the first elastic portion 21 is greater than or equal to a preset stiffness, and the stiffness of the second elastic portion 22 is less than the preset stiffness. The lift limiter 30 is mounted on the valve seat 10 and includes a limiting structure located above the valve plate 20. The first elastic portion 21 and the second elastic portion 22 of the valve plate 20 are used to bend the valve plate 20 away from the valve seat 10 to release the exhaust port 11.

[0044] Specifically, the valve seat 10 is provided with an exhaust port 11 to realize compressor exhaust, and the valve seat 10 is integrated with the compressor bearing. The valve plate 20 is provided with a first end installed on the valve seat 10 and a second end covering the exhaust port 11. The first end of the valve plate 20 is a flat fixed part at the tail end, and is fixedly installed on the valve seat 10 by fasteners such as rivets 12 to form a support base. The second end of the valve plate 20 is a head, and the size of the second end is greater than or equal to the exhaust port 11 to cover or release the exhaust port 11, thereby realizing the on-off control of compressor exhaust. The valve plate 20 includes a first elastic part 21 near the first end and a second elastic part 22 near the second end. The stiffness of the first elastic part 21 is greater than or equal to a preset stiffness, and the stiffness of the second elastic part 22 is less than the preset stiffness. The two are structurally transitioned to form an integral elastic structure. At the same time, the lift limiter 30 is also installed on the valve seat 10 and located above the valve plate 20. The lift limiter 30 has a limit structure corresponding to the position of the valve plate 20, which is used to limit the lifting height of the second end of the valve plate 20, and at the same time provides an auxiliary force during the rebound of the valve plate 20 to accelerate the reset of the valve plate 20.

[0045] When the compressor operates at a low frequency, such as in low-frequency operation, the gas pressure discharged from the exhaust port 11 is low, which only triggers the second elastic part 22 of the valve plate 20, while the first elastic part 21 remains unchanged. At this time, the second elastic part 22 bends independently away from the valve seat 10, causing the second end to lift and release the exhaust port 11. Because the second elastic part 22 has low stiffness, and in conjunction with the lift limiter 30 limiting the lifting height, it ensures that the valve plate 20 is triggered to open in time, while delaying the rebound speed of the valve plate 20 to avoid the problem of gas overcompression caused by premature closure.

[0046] When the compressor operates at a high frequency, such as in high-frequency operation, the gas pressure discharged from the exhaust port 11 increases. This can simultaneously trigger the first elastic part 21 and the second elastic part 22, causing them to bend together in the direction away from the valve seat 10. This causes the second end to rise and release the exhaust port 11. At this time, due to the high rigidity of the first elastic part 21, combined with the limiting effect of the lift limiter 30, it can ensure that the valve plate 20 rebounds in time to close the exhaust port 11 at the end of the exhaust process, preventing high-pressure refrigerant from flowing back into the cylinder, thereby reducing secondary compression losses.

[0047] As can be seen, by using the exhaust valve assembly for the compressor provided in this application, the differential stiffness design of the first elastic part 21 and the second elastic part 22, as well as the limiting and auxiliary rebound function of the lift limiter 30, can adapt to the operating requirements of the compressor at different frequencies: at low frequencies, it ensures sufficient exhaust and reduces over-compression; at high frequencies, it avoids closing delay and reduces backflow loss, ultimately achieving the effect of increasing the cooling capacity of the refrigeration equipment and reducing the input power of the compressor.

[0048] In the above embodiments, the preset stiffness can be set according to the user's actual needs, as long as it meets the requirements of the valve plate 20 to match the exhaust demand at different frequencies, ensuring that the valve plate 20 opens in a timely manner and closes with a delay at low frequencies, and opens fully and closes in a timely manner at high frequencies. For example, the preset stiffness can be set according to factors such as the exhaust pressure, exhaust cycle, lift limit parameters, valve plate 20 structural dimensions, and energy efficiency targets at different frequencies of the compressor.

[0049] In some practical applications, the valve plate 20 is configured as a reed structure.

[0050] In some practical applications, the lift limiter 30 is configured to be made of spring steel, PEEK (polyether ether ketone), or a high-performance engineering plastic with equivalent properties to meet the requirements for elasticity and rigidity.

[0051] like Figure 4 As shown, in some embodiments, the first elastic portion 21 and the second elastic portion 22 of the valve plate 20 are configured as an integrally formed structure; the width of the first elastic portion 21 is greater than the width of the second elastic portion 22.

[0052] Specifically, the first elastic portion 21 and the second elastic portion 22 of the valve plate 20 adopt an integral molding structure, which is formed by processing a whole material in one go, ensuring the structural continuity and mechanical stability of the connection between the two, and avoiding stress concentration problems caused by separate connection. Furthermore, the width of the first elastic portion 21 is greater than the width of the second elastic portion 22. Specifically, taking the length direction of the valve plate 20 as a reference, the first transverse width W1 of the first elastic portion 21 and the second transverse width W2 of the second elastic portion 22 satisfy W1 > W2.

[0053] Understandably, given the same material properties and thickness, the wider the elastic part, the stronger its bending resistance, i.e., the higher its stiffness. Therefore, the first elastic part 21 achieves a stiffness higher than the preset value through its larger width, while the second elastic part 22 achieves a stiffness lower than the preset value through its smaller width. This stiffness differentiation can be achieved without the need for a complex additional rigidity adjustment structure. It can be seen that the valve plate 20, employing the aforementioned one-piece molded width differentiation design, achieves stiffness differentiation through a simple structure while ensuring the overall structural strength and service life of the valve plate 20. This adapts to the full-frequency operation requirements of the compressor, simplifying the manufacturing process while optimizing exhaust performance.

[0054] like Figure 4 As shown, in some embodiments, the first end and the second end of the first elastic portion 21 are respectively connected to the first end of the valve plate 20 and the second elastic portion 22; wherein, the width of the first elastic portion 21 gradually increases from the second end to the first end.

[0055] Specifically, the first elastic part 21 of the valve plate 20 adopts a gradually changing width design. Its first end is connected to the fixed end of the valve plate 20, that is, the valve plate 20 is installed at one end of the valve seat 10, and the second end is connected to the second elastic part 22. From the second end to the first end, the width of the first elastic part 21 gradually increases, forming a smoothly transitioning wedge or trapezoidal structure. The width change area is connected by a continuous straight line or arc surface to avoid stress concentration caused by right angle or abrupt structure.

[0056] Understandably, the side of the first elastic part 21 closest to the second elastic part 22 has a narrower width and lower stiffness, while the side closest to the first end of the valve plate 20 has a wider width and higher stiffness, thus forming a stiffness gradient from low to high. This arrangement allows for a smooth transition with the low stiffness characteristic of the second elastic part 22 while ensuring that the overall stiffness of the first elastic part 21 is higher than a preset value. It can be seen that the aforementioned gradient width design achieves stiffness gradient adjustment through continuous changes in structural parameters, ensuring both the mechanical matching of the first elastic part 21 and the second elastic part 22, and adaptively selecting different stiffness regions according to the exhaust pressure, further optimizing the opening and closing performance of the valve plate 20 across the entire frequency band.

[0057] like Figure 4 As shown, in some embodiments, the second end of the valve plate 20 is configured as a circle, and the diameter of the second end of the valve plate 20 is a first diameter d; the distance from the first end of the first elastic part 21 to the second end of the valve plate 20 is a first length L, and the distance from the second end of the first elastic part 21 to the second end of the valve plate 20 is a second length l; wherein, 0.38L+d≤l≤0.6L+d.

[0058] Specifically, the distance from the side of the first elastic part 21 near the fixed end of the valve plate 20 to the second end of the valve plate 20 is a first length L, which corresponds to the overall cantilever length of the valve plate 20, i.e., the effective force-bearing length of the valve plate 20 from the fixed base point to the head edge. The distance from the side of the first elastic part 21 near the second elastic part 22 to the second end of the valve plate 20 is a second length l, which corresponds to the effective deformation length of the second elastic part 22 and the first elastic part 21 near the head region. For example, the second length l can be 0.38L+d, 0.5L+d, 0.55L+d, or 0.6L+d.

[0059] Understandably, the first length L, as the overall cantilever length, needs to be coordinated with the stiffness design of the first elastic part 21. During high-frequency operation, exhaust pressure pushes both the first elastic part 21 and the second elastic part 22 to bend together. The first length L determines the leverage effect of the overall structure and needs to work in conjunction with the high stiffness characteristics of the first elastic part 21 to ensure that the valve plate 20 head can rise to the second lift limit of the lift limiter 30, and that it can quickly rebound due to overall rigidity at the end of exhaust, avoiding closing delay. The second length l needs to ensure that the deformation range of the second elastic part 22 matches the requirements of low-frequency operation. During low-frequency operation, exhaust pressure only triggers the bending of the second elastic part 22. At this time, the second length l determines the cantilever leverage ratio of the second elastic part 22, requiring sufficiently low stiffness in this area to ensure that the valve plate 20 head can rise to the first lift limit of the lift limiter 30.

[0060] like Figures 1 to 6 As shown, in some embodiments, the limiting structure of the lift limiter 30 includes a first limiting part 31 and a second limiting part 32. The first limiting part 31 is located on the side of the second limiting part 32 close to the valve plate 20, and the size of the second limiting part 32 is larger than the size of the first limiting part 31.

[0061] Specifically, the lift limiter 30 is installed on the valve seat 10, and a limiting structure for limiting the maximum lifting height of the valve plate 20 is provided on one side of the valve plate 20. The limiting structure includes a first limiting part 31 and a second limiting part 32, and the first limiting part 31 is located on the side of the second limiting part 32 closer to the valve plate 20. The size of the second limiting part 32 being larger than the size of the first limiting part 31 means that the size of the second limiting part 32 in the length direction or the width direction is larger than that of the first limiting part 31, so as to form a stepped structure with a small range of limiting at the lower level and a large range of limiting at the upper level.

[0062] When the compressor operates at low frequency, the discharge pressure on the valve plate 20 is relatively low, resulting in a lower lifting height and smaller bending amplitude. At this time, after the valve plate 20 bends upwards to contact the first limiting part 31, it is restricted from further lifting by the first limiting part 31, and the lift is limited to a range suitable for low-frequency performance. When the compressor operates at high frequency, the discharge pressure increases, and the lifting height and bending amplitude of the valve plate 20 increase significantly. At this time, the portion of the valve plate 20 near the second end and exceeding the coverage of the first limiting part 31 is no longer restricted from continuing to bend upwards by the first limiting part 31. Due to the coverage of the second limiting part 32, the valve plate 20 eventually contacts the second limiting part 32 and is restricted to a higher lift range.

[0063] like Figure 3 As shown, in some embodiments, the distance from the first limiting part 31 to the valve plate 20 is a first height h1, and the distance from the second limiting part 32 to the valve plate 20 is a second height h2; wherein, 0.4h2≤h1≤0.75h2.

[0064] Specifically, the distance from the first limiting part 31 to the initial position (unopened state) of the valve plate 20 is the first height h1, and the distance from the second limiting part 32 to the initial position of the valve plate 20 is the second height h2, and 0.4h2≤h1≤0.75h2. For example, h1 can be 0.4h2, 0.5h2, 0.6h2, 0.7h2, or 0.75h2.

[0065] Understandably, the first height h1 corresponds to the lift threshold under low-frequency operating conditions. When the compressor is operating at low frequency (e.g., 30Hz), the discharge pressure is relatively low, and only the second elastic part 22 of the valve plate 20 bends. The lifting height is limited by the first limiting part 31. At this time, the value of the first height h1 needs to ensure that the lift of the valve plate 20 matches the stable range of resistance loss under low frequency. By setting h1≤0.75h2, it can be ensured that the low-frequency lift is lower than the high-frequency lift, avoiding the problem of premature closure caused by excessive lifting of the valve plate 20 at low frequency, and reducing over-compression loss. The second height h2 corresponds to the lift threshold under high-frequency operating conditions. When the compressor is operating at high frequency (e.g., 90Hz), the discharge pressure increases, and the first elastic part 21 and the second elastic part 22 of the valve plate 20 bend together. The lifting height is limited by the second limiting part 32. At this time, the second height h2 needs to meet the lift requirement for stable resistance loss under high frequency. By setting h1≥0.4h2, it can be ensured that the low-frequency lift is not too small, avoiding the increase in low-frequency exhaust resistance due to insufficient lift, and balancing the exhaust efficiency across the entire frequency range.

[0066] like Figures 1 to 6 As shown, in some embodiments, the second height h2 is greater than or equal to 2.5 mm and less than or equal to 4 mm.

[0067] Specifically, the distance from the second limiting part 32 to the initial position of the valve plate 20, i.e., the second height h2, is configured to satisfy a size range of 2.5mm ≤ h2 ≤ 4mm. For example, the second height h2 can be 2.5mm, 3mm, 3.5mm, or 4mm.

[0068] Understandably, when the compressor is operating at high frequency, the refrigerant flow is large and the discharge speed is fast, requiring a larger lift to reduce discharge resistance. If h2 < 2.5 mm, the valve plate 20 will not lift sufficiently at high frequency, resulting in excessive discharge resistance loss and increasing the compressor's input power. If h2 > 4 mm, excessive lifting of the valve plate 20 will lead to excessive bending deformation, and the excessive lift will prolong the valve plate 20 closing time, increasing the risk of high-pressure refrigerant backflow.

[0069] In some embodiments, the first limiting portion 31 is configured as an elastic material; the second limiting portion 32 is configured as a rigid material.

[0070] Specifically, the first limiting part 31 is made of an elastic material, such as spring steel, high-elasticity alloy, or engineering plastic with resilience; the second limiting part 32 is made of a rigid material, such as high-strength steel, PEEK, or other high-performance rigid engineering plastics. This arrangement allows for the adaptation to limiting requirements at different frequencies through differentiated design of material properties.

[0071] Understandably, the first limiting part 31, as the main limiting structure under low-frequency operating conditions, uses an elastic material to achieve flexible limiting. When the compressor operates at low frequency, the valve plate 20 is raised to a low height. When it comes into contact with the first limiting part 31, the elastic material undergoes slight deformation to buffer the contact impact force. On the one hand, this reduces the rigid collision loss between the valve plate 20 and the limiting part, reducing wear caused by high-frequency contact. On the other hand, the rebound force generated by the elastic deformation is relatively gentle, which can cooperate with the low stiffness characteristics of the second elastic part 22 of the valve plate 20 to delay the closing speed of the valve plate 20, preventing the valve plate 20 from closing prematurely due to rigid collision at low frequencies, and further improving the over-compression problem. The second limiting part 32, as the limiting structure under high-frequency operating conditions, uses a rigid material to provide stable rigid support. During high-frequency operation, the valve plate 20 experiences a large lifting height and strong impact force. The rigid material precisely limits the maximum lift of the valve plate 20, preventing uncontrolled lift due to material deformation. Simultaneously, the rigid material generates a significant instantaneous reaction force upon contact, accelerating the rebound and closure of the valve plate 20 at the end of exhaust, preventing backflow of high-pressure refrigerant. It can be seen that the elastic material of the first limiting part 31 is adapted to the small amplitude, high-frequency contact of the valve plate 20 at low frequencies, reducing wear and assisting in delayed closure; the rigid material of the second limiting part 32 is adapted to the large amplitude, strong impact contact of the valve plate 20 at high frequencies, ensuring precise lift and assisting in rapid closure.

[0072] In some embodiments, the connection between the first end of the valve plate 20 and the first elastic portion 21 is configured with an arc-shaped chamfer structure; the connection between the first elastic portion 21 and the second elastic portion 22 is configured with an arc-shaped chamfer structure.

[0073] Specifically, the connection between the first end of the valve plate 20 and the first elastic part 21, and the connection between the first elastic part 21 and the second elastic part 22, are all designed with an arc-shaped chamfer structure. The connection between the first end of the valve plate 20 and the first elastic part 21 is replaced by a rounded transition instead of a right angle or an acute angle. The radius of the rounded transition is set according to the overall size of the valve plate 20.

[0074] Understandably, the connection between the first end of the valve plate 20 and the first elastic part 21 is the main stress-bearing area under low-frequency operating conditions. When the compressor operates at low frequency, only the second elastic part 22 of the valve plate 20 bends, while the first elastic part 21 remains relatively stable. This area serves as the transition between the fixed end and the elastic part of the valve plate 20. If a right-angle structure is used here, stress concentration is likely to occur. The arc-shaped chamfer can evenly distribute the stress along the arc surface, reducing the risk of fatigue fracture under long-term low-frequency operation. The connection between the first elastic part 21 and the second elastic part 22 is the core deformation transition area under high-frequency operating conditions. During high-frequency operation, both bend together and have different stiffnesses. A right-angle connection would cause stress concentration at the corner during deformation. The arc-shaped chamfer, through a smooth transition, makes the stress gradient in the stiffness change area more gradual, avoiding material fatigue caused by frequent bending, while ensuring that the bending deformation proceeds along a preset path, thus ensuring the effectiveness of the graded stiffness design.

[0075] like Figures 1 to 6 As shown, this disclosure also provides a compressor including the above-described exhaust valve assembly for a compressor.

[0076] Specifically, the compressor includes the aforementioned discharge valve assembly. The valve seat 10 is provided with a discharge port 11 to enable compressor discharge, and the valve seat 10 is integrated with the compressor bearing. The compressor using the discharge valve assembly provided in this application can adapt to the operating requirements of the compressor at different frequencies through differentiated stiffness design of the first elastic part 21 and the second elastic part 22, as well as the limiting and auxiliary rebound functions of the lift limiter 30: ensuring sufficient discharge and reducing over-compression at low frequencies; avoiding shutdown delay and reducing backflow losses at high frequencies, ultimately achieving the effect of increasing the cooling capacity of the refrigeration equipment and reducing the compressor input power.

[0077] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. An exhaust valve assembly for a compressor, characterized in that, include: Valve seat (10) is provided with an exhaust port (11); The valve plate (20) is provided with a first end installed on the valve seat (10) and a second end covered on the exhaust port (11). The valve plate (20) includes a first elastic part (21) near the first end and a second elastic part (22) near the second end. The stiffness of the first elastic part (21) is greater than or equal to a preset stiffness, and the stiffness of the second elastic part (22) is less than the preset stiffness. and, A lift limiter (30) is installed on the valve seat (10), the lift limiter (30) including a limiting structure located above the valve plate (20); The first elastic portion (21) and the second elastic portion (22) of the valve plate (20) are used to bend the valve plate (20) away from the valve seat (10) to release the exhaust port (11).

2. The exhaust valve assembly according to claim 1, characterized in that, The first elastic portion (21) and the second elastic portion (22) of the valve plate (20) are configured as an integrally formed structure; and, The width of the first elastic part (21) is greater than the width of the second elastic part (22).

3. The exhaust valve assembly according to claim 2, characterized in that, The first end and the second end of the first elastic part (21) are respectively connected to the first end of the valve plate (20) and the second elastic part (22); The width of the first elastic part (21) gradually increases from the second end to the first end.

4. The exhaust valve assembly according to claim 1, characterized in that, The second end of the valve plate (20) is configured to be circular, and the diameter of the second end of the valve plate (20) is a first diameter d; and, The distance from the first end of the first elastic part (21) to the second end of the valve plate (20) is a first length L, and the distance from the second end of the first elastic part (21) to the second end of the valve plate (20) is a second length l; Wherein, 0.38L+d≤l≤0.6L+d.

5. The exhaust valve assembly according to claim 1, characterized in that, The limiting structure of the lift limiter (30) includes a first limiting part (31) and a second limiting part (32). The first limiting part (31) is located on the side of the second limiting part (32) close to the valve plate (20), and the size of the second limiting part (32) is larger than the size of the first limiting part (31).

6. The exhaust valve assembly according to claim 5, characterized in that, The distance from the first limiting part (31) to the valve plate (20) is a first height h1, and the distance from the second limiting part (32) to the valve plate (20) is a second height h2; Where 0.4h2≤h1≤0.75h2.

7. The exhaust valve assembly according to claim 6, characterized in that, The second height h2 is greater than or equal to 2.5 mm and less than or equal to 4 mm.

8. The exhaust valve assembly according to claim 5, characterized in that, The first limiting part (31) is made of an elastic material; and, The second limiting part (32) is made of a rigid material.

9. The exhaust valve assembly according to any one of claims 1 to 8, characterized in that, The connection between the first end of the valve plate (20) and the first elastic part (21) is configured with an arc-shaped chamfer structure; and, The connection between the first elastic part (21) and the second elastic part (22) is configured as an arc-shaped chamfer structure.

10. A compressor, characterized in that, include: The exhaust valve assembly for a compressor as described in any one of claims 1 to 9.

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