Exhaust valve, cylinder assembly, compressor and refrigeration device

Abstract

The embodiment of the present application provides an exhaust valve plate, a cylinder assembly, a compressor and a refrigeration equipment. The exhaust valve plate comprises a valve plate head, a valve plate tail and a deformation section, the deformation section is located between the valve plate head and the valve plate tail to connect the valve plate head and the valve plate tail; the valve plate tail is configured to be connected to a cylinder cover of a cylinder, the valve plate head is configured to be oppositely arranged with an exhaust valve hole of the cylinder cover and can move relative to the cylinder cover to open or close the exhaust valve hole. In the process of moving relative to the cylinder cover to open the exhaust valve hole, when a reference point Q is lifted to a lift height h, the elastic force F1 received by the valve plate head and the lift height h satisfy the following relationship: 1.5 <= F1 / h <= 2.2; 1.5mm <= h <= 2.3mm; wherein the unit of the elastic force F1 is N. The exhaust valve plate provided by the embodiment of the present application improves the dynamic response characteristic of the exhaust valve plate, thereby improving the energy efficiency of the compressor and reducing the noise of the compressor.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and in particular to an exhaust valve plate, cylinder assembly, compressor and refrigeration equipment. Background Technology

[0002] In air conditioning systems, the compressor is the core power component, and its performance directly affects the overall cooling efficiency and operating noise. Compressors typically employ a rolling rotor structure, using the relative motion between the rotor and cylinder to compress and discharge the refrigerant.

[0003] During compression, the exhaust valve, as a key component controlling refrigerant discharge, needs to open and close frequently under the influence of the pressure difference between the inside and outside of the cylinder. The exhaust valve needs to maintain stable operation in high-temperature and high-pressure environments, and its dynamic response characteristics directly determine the compressor's energy efficiency and noise level.

[0004] However, the dynamic response characteristics of the exhaust valve plate in the related technology are insufficient. Summary of the Invention

[0005] This application provides an exhaust valve plate, a cylinder assembly, a compressor, and a refrigeration device, which improves the dynamic response characteristics of the exhaust valve plate, thereby improving the energy efficiency of the compressor and reducing the noise of the compressor.

[0006] In a first aspect, embodiments of this application provide an exhaust valve plate, which includes a valve plate head and a valve plate tail. The valve plate tail is configured to be connected to the cylinder head of a cylinder. The valve plate head is configured to be disposed opposite to an exhaust valve hole on the cylinder head and can move relative to the cylinder head to open or close the exhaust valve hole. When the valve plate head closes the exhaust valve hole, the point opposite to the center of the valve plate head and the center of the exhaust valve hole is recorded as reference point Q.

[0007] During the process of the valve head moving relative to the cylinder head to open the exhaust valve orifice, when the reference point Q is raised to the lift height h, the elastic force F1 on the valve head and the lift height h satisfy the following relationship: 1.5≤F1 / h≤2.2; 1.5mm≤h≤2.3mm; where the unit of elastic force F1 is N.

[0008] The exhaust valve plate provided in this embodiment has its tail fixedly connected to the cylinder head of the cylinder, and its head corresponding to the exhaust valve hole on the cylinder head to control the opening and closing of the exhaust valve hole. The tail of the exhaust valve plate is connected to the deformation section of the valve head, thereby providing elastic support for the movement of the valve head. During the compressor's exhaust process, the exhaust valve plate is pushed open by the high-pressure gas, the deformation section deforms, and the valve head moves away from the exhaust valve hole, thereby opening the exhaust valve hole. As the gas pressure inside the cylinder decreases, the exhaust valve plate rebounds, causing the valve head to seal the exhaust valve hole, thereby closing the exhaust valve hole.

[0009] In this embodiment, the lift height h of the exhaust valve plate is limited to between 1.5 and 2.3 mm, so that when the exhaust valve plate opens the exhaust valve orifice, the exhaust flow area is sufficient, which can effectively reduce the gas discharge resistance, reduce over-compression loss, and improve the exhaust efficiency and energy efficiency of the compressor. At the same time, within the above range, the bending stress of the exhaust valve plate is moderate, which can effectively avoid the problem of reduced fatigue life caused by excessive lift. The sitting impact is also within a controllable range, which helps to reduce the impact noise between the exhaust valve plate and the cylinder head during the return process.

[0010] Meanwhile, in this embodiment, the value of F1 / h is limited to the range of 1.5 to 2.2, which enables the elastic characteristics of the valve plate to be coordinated with the pressure pulsation during the compressor's discharge process. This ensures that the discharge valve plate responds quickly to the pressure pulsation of the compressor's discharge, helping to avoid poor discharge and over-compression losses caused by delayed opening. At the same time, it also helps to ensure that the discharge valve plate closes in time after the discharge is completed, reducing the phenomenon of high-pressure gas backflow. This improves the dynamic response characteristics of the discharge valve plate and adapts to the high-frequency operation requirements of the compressor.

[0011] Therefore, by limiting the value of F1 / h and the lift height h, this embodiment ensures that the elastic force F1 and the lift height h on the valve head satisfy: 1.5≤F1 / h≤2.2, 1.5≤h≤2.3. This optimizes the dynamic response characteristics of the valve opening and closing, ensuring rapid opening and timely closing of the valve, reducing backflow loss and impact noise, controlling the bending stress of the valve, extending fatigue life, improving the performance of the compressor unit, and reducing the operating noise of the compressor. As a result, this exhaust valve can be used with compressors with a cooling capacity of 2500W-3700W and covers most conventional operating conditions.

[0012] In some embodiments, the exhaust valve plate further includes a deformation section located between the valve plate head and the valve plate tail to connect the valve plate head and the valve plate tail.

[0013] With the center of the exhaust valve orifice as the central axis, the average diameter corresponding to each differential circular arc segment in the valve plate head is taken as the diameter of the valve plate head, denoted as d1. The average width of the deformation segment is taken as W1, and the length of the deformation segment is taken as L1. The arrangement direction of the valve plate head, deformation segment, and valve plate tail is the length direction of the exhaust valve plate. The total length of the exhaust valve plate is taken as L2, and the thickness of the exhaust valve plate is taken as t. The units of d1, W1, L1, L2, and t are all mm, and the following condition is satisfied:

[0014]

[0015] Where E is the elastic modulus of the exhaust valve plate, in GPa; S is the first correction factor, and S is the shape factor. S is determined based on the structure of the valve head; the structure of the valve head includes a fan-shaped structure, a circular structure, or a first shape structure, the first shape structure including other shape structures besides the fan-shaped structure and the circular structure;

[0016] The fan-shaped structure, circular structure, and first shape structure correspond to different Furthermore, the fan-shaped structure, the circular structure, and the first shape structure each correspond to different S.

[0017] The conditional expression in this application embodiment can express the theoretical elastic force value when the exhaust valve plate elastically deforms to the lift height h. This theoretical value is compared with the range of F1 / h and h values ​​defined in this application embodiment. If the theoretical value is within this range, it can be preliminarily determined that the design scheme meets the stiffness requirements. If the theoretical value exceeds this range, it can be recalculated and verified by adjusting geometric parameters or material properties until the theoretical value meets the requirements, and then experimental measurement verification can be performed, thereby shortening the design cycle and reducing experimental costs.

[0018] In some embodiments, when the valve disc head has a fan-shaped structure... =32, S=1.1.

[0019] In this embodiment, the first correction coefficient It is mainly used to correct the influence of uneven stress on stiffness calculation of the sector structure. The shape factor S is used to adapt to the contour characteristics of the sector structure, compensate for the deformation difference between its edge area and center area, and ensure that the theoretical calculation can accurately reflect the actual stiffness characteristics of the sector structure valve plate.

[0020] In some embodiments, the fan-shaped structure has two intersecting first sides, both of which are circular arc edges with a radius of R1, and the included angle between the two first sides is α, wherein 60mm≤R1≤100mm and 15°≤α≤75°.

[0021] In this embodiment, when the included angle α is limited to between 15° and 75°, the effective coverage area of ​​the valve head and the stress adaptation of the transition area are well matched. This ensures that the exhaust valve orifice is completely covered by a reasonable coverage area, meeting the sealing requirements of exhaust valves of different specifications, while also maintaining a moderate width in the transition area and evenly distributing stress along the arc edge, thus helping to avoid stress concentration. Simultaneously, α within this range allows for a reasonable mass distribution of the fan-shaped head, which helps ensure that the F1 / h ratio remains stable within the range of 1.5 to 2.2. This allows for a good and rapid response to exhaust pressure pulsations to open the valve, and also enables timely closing to reduce backflow loss and impact noise.

[0022] In some embodiments, when the valve head has a circular structure... =25, S=0.9.

[0023] In this embodiment, because the shape of the circular valve head differs from that of the aforementioned fan-shaped structure, there is a difference between the first correction factor and the shape factor. The first correction factor k is primarily used to correct the influence of the circular structure on stiffness calculations and compensate for the stress transfer differences between the circular head and the transition region of the deformation segment. The shape factor S is used to adapt to the contour characteristics of the circular structure, correct the correlation between the area of ​​the circular head and the stress efficiency, and ensure that theoretical calculations accurately reflect the actual stiffness characteristics of the circular exhaust valve head, providing a reliable basis for stiffness prediction during the design phase.

[0024] In some embodiments, the circular structure has two opposing second sides on the side facing the deformation segment. Both second sides are circular arc edges with a radius of R2, where R2 is in mm. R2 and d1 satisfy the following relationship: 0.05≤R2 / d1≤2.5.

[0025] This embodiment achieves a smooth transition between the circular head and the deformation section by setting two opposing arc-shaped second sides with a radius of R2 on the side of the circular valve plate head facing the deformation section, and limiting the value of R2 / d1 to 0.05~2.5. This optimizes the stress transmission path, effectively avoids stress concentration, and takes into account structural strength, effective stress-bearing area and overall valve plate size. Combined with the aforementioned k, S values ​​and stiffness parameter limitations, the design of the circular exhaust valve plate is further improved, enhancing its operational reliability, dynamic response characteristics and adaptability. It can better meet the exhaust requirements of compressors of different specifications and provide strong support for the efficient and low-noise operation of the compressor.

[0026] In some embodiments, when the structure of the valve disc head is a first shape structure... =30, S=1.0, so that when the first shape structure is other shapes, the stiffness K of the exhaust valve plate of the valve plate head with other shape structure can be theoretically calculated.

[0027] In some embodiments, the exhaust valve plate is disposed on a compressor including a cylinder, and the compressor operates at an operating frequency of 120 Hz and an exhaust pressure of 2.93 MPa, and d1, W1, L1, L2, and t satisfy the following conditional expression:

[0028]

[0029] Where ρ is the material density of the exhaust valve plate, in g / cm³, and e is the natural constant, taken as 2.718.

[0030] In this embodiment, the conditional expressions satisfied by the parameters of the exhaust valve disc can be the range of the theoretical elastic force value experienced by the valve disc head. During the exhaust valve disc design phase, the corresponding first correction coefficient is determined based on the selected valve disc head structure, elastic modulus E, and various geometric parameters. Substituting the shape factor S into the above formula, we can calculate the theoretical elastic force on the valve head when the reference point Q is raised to the lift height h.

[0031] The theoretical value is compared with the range of F1 / h and h values ​​defined in the embodiments of this application. If the theoretical value is within the range, it can be preliminarily determined that the design scheme meets the stiffness requirements. If the theoretical value exceeds the range, the geometric parameters or material properties can be adjusted, and the calculation and verification can be repeated until the theoretical value meets the requirements. Then, experimental measurement and verification can be carried out, thereby shortening the design cycle and reducing the experimental cost.

[0032] In some embodiments, L1 and d1 satisfy the following relationship: 0.7 ≤ L1 / d1 ≤ 1.4.

[0033] In this embodiment, the L1 / d1 ratio limitation can balance sealing performance and stiffness stability, avoiding both an increase in impact torque caused by an excessively large valve head and a sealing failure caused by an excessively small valve head. Combined with the L1 / L2 ratio limitation, the overall structural dimensions of the valve can be further optimized, resulting in a more uniform stress distribution, reduced fatigue damage, and improved fatigue life of the exhaust valve.

[0034] In some embodiments, L1 and L2 satisfy the following relationship: 0.3≤L1 / L2≤0.5.

[0035] This embodiment of the application limits the ratio of L1 to L2 to a range of 0.3 to 0.5, which can effectively balance the elastic stroke, structural strength and dynamic stability of the exhaust valve plate. This ensures that the valve plate has sufficient elastic stroke to achieve good stiffness adjustment, and also ensures that the fixed end has sufficient strength for reliable installation, so as to make the stress distribution more uniform and thus improve the fatigue life of the valve plate.

[0036] In some embodiments, the average width of the valve plate tail is W2, and W2 and the average width W1 of the deformed section satisfy the following condition: 0.2≤W1 / W2≤0.8.

[0037] This embodiment, by limiting the ratio of W1 / W2 to a range of 0.2 to 0.8, can effectively achieve a smooth width transition from the tail of the valve plate to the deformation section, optimize the stress distribution at the bend of the valve plate tail, avoid fatigue failure caused by stress concentration, and at the same time ensure the flexibility of the deformation section to provide a suitable elastic force F, thereby improving its operational reliability, dynamic response characteristics and adaptability under long-term cyclic loads, and providing strong support for the efficient and low-noise operation of the compressor.

[0038] In some embodiments, the thickness t of the exhaust valve plate satisfies the following condition: 0.25mm≤t≤0.45mm.

[0039] This application embodiment limits the thickness t of the exhaust valve plate to the range of 0.25~0.45mm, which helps to control the elasticity F1 of the valve plate, balance the impact resistance and opening and closing flexibility of the valve plate, and, together with the aforementioned parameter design, further improves the overall design of the exhaust valve plate, enhances its operational reliability, dynamic response characteristics, energy efficiency and service life, and provides strong support for the efficient, low-noise and stable operation of the compressor.

[0040] Secondly, embodiments of this application provide a cylinder assembly, including:

[0041] The cylinder block;

[0042] The cylinder head, with the cylinder head seat cover located on top of the cylinder block, has an exhaust valve hole;

[0043] The exhaust valve plate mentioned above has its tail end connected to the cylinder head, and its head end positioned opposite the exhaust valve port, and can move relative to the cylinder head to open or close the exhaust valve port.

[0044] The cylinder assembly provided in this embodiment can reduce the operating noise of the cylinder assembly and improve the operating reliability of the cylinder assembly through the aforementioned exhaust valve plate.

[0045] Thirdly, embodiments of this application provide a compressor, including the above-mentioned exhaust valve plate, or including the above-mentioned cylinder assembly, the cylinder assembly being disposed within a cylinder body.

[0046] The compressor provided in this embodiment can improve energy efficiency and reduce operating noise through the aforementioned exhaust valve plate.

[0047] Fourthly, embodiments of this application provide a refrigeration device, including the aforementioned exhaust valve plate, or the aforementioned cylinder assembly, or the aforementioned compressor.

[0048] The compressor refrigeration equipment provided in this embodiment can improve energy efficiency and reduce operating noise through the aforementioned exhaust valve plate. Attached Figure Description

[0049] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0050] Figure 1 This is a schematic diagram of the cylinder assembly provided in an embodiment of this application;

[0051] Figure 2 for Figure 1Cross-sectional view of the cylinder assembly;

[0052] Figure 3 This is a schematic diagram of the structure of the exhaust valve plate provided in the embodiments of this application;

[0053] Figure 4 This is a schematic diagram of another exhaust valve plate provided in an embodiment of this application;

[0054] Figure 5 A side view of the exhaust valve plate provided in an embodiment of this application;

[0055] Figure 6 A diagram showing the relationship between compressor performance and exhaust valve plate stiffness provided in an embodiment of this application;

[0056] Figure 7 A graph showing the relationship between compressor operating noise and exhaust valve plate stiffness provided in an embodiment of this application;

[0057] Figure 8 A graph showing the relationship between compressor performance and effective mass of the exhaust valve plate is provided for an embodiment of this application.

[0058] Figure 9 A graph showing the relationship between compressor operating noise and effective mass of the exhaust valve plate, provided for an embodiment of this application.

[0059] Figure label:

[0060] 10-Cylinder head; 11-Exhaust valve port;

[0061] 20-Exhaust valve plate; 21-Valve plate head; 211-First side; 212-Second side; 22-Deformation section; 23-Valve plate tail. Detailed Implementation

[0062] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0063] This application provides a refrigeration device that can be used to cool enclosed spaces. For example, the refrigeration device can be an air conditioner, central air conditioning system, refrigerator, heat pump, or chiller.

[0064] Refrigeration equipment typically includes a compressor. A compressor converts low-temperature, low-pressure gas into high-temperature, high-pressure gas, thereby enabling the refrigerant cycle within a refrigeration or heat pump system. The compressor can be a scroll compressor, a rotary compressor, or a reciprocating compressor.

[0065] The following example uses a reciprocating compressor. A compressor may include a piston and cylinder assembly. See also... Figure 1 and Figure 2 The cylinder assembly provided in this application embodiment may include a cylinder, a cylinder head 10, and an exhaust valve plate 20. A piston is disposed within the inner cavity of the cylinder body to compress the gas within the cylinder body. The cylinder head 10 is disposed on the top of the cylinder body and has an exhaust valve hole 11. The exhaust valve plate 20 is disposed on the cylinder head 10 corresponding to the exhaust valve hole 11. During compressor operation, the piston undergoes elastic deformation under pressure changes within the cylinder, thereby controlling the opening and closing of the exhaust hole.

[0066] Specifically, when air enters the cylinder, the exhaust valve plate 20 blocks the exhaust valve hole 11, allowing low-pressure refrigerant to enter the cylinder. As the piston slides, it compresses the refrigerant gas, increasing its pressure and temperature. When the gas pressure inside the cylinder exceeds the opening pressure of the exhaust valve at the top of the cylinder, the high-pressure gas can push open the exhaust valve plate 20 and exit the compressor through the exhaust valve hole 11.

[0067] Therefore, the timeliness and smoothness of the opening and closing of the exhaust valve plate 20 directly affect the smooth discharge and effective sealing of high-pressure gas, thereby influencing the compressor's discharge efficiency, operating energy efficiency, noise level, and operational reliability. Specifically, the exhaust valve plate 20 needs to respond quickly to the discharge pressure when opening to reduce over-compression losses; and when closing, it needs to seal the exhaust valve orifice 11 in a timely manner to prevent high-pressure gas backflow and valve plate vibration, thereby reducing noise and extending service life. In addition, the exhaust valve plate 20 also needs to withstand high-frequency pulsating aerodynamic forces and opening and closing impacts. Its structural design needs to take into account both lightweight and fatigue resistance characteristics to meet the requirements of air conditioning for high energy efficiency, low noise, and long service life.

[0068] In related technologies, exhaust valve plate design typically optimizes valve plate performance by adjusting a single parameter (such as thickness or length). Specifically, exhaust valve plate stiffness is mainly controlled by changing the material thickness or the length of the deformation section, while the effective mass adjustment depends on changes in the shape of the valve plate head or the width of the tail. However, this parameter adjustment method easily leads to insufficient coordination between stiffness and effective mass, resulting in a lag in the dynamic response of the valve plate during opening and closing, making it unable to adapt to the high-frequency operation requirements of the compressor, and consequently causing energy efficiency reduction and high-pressure gas backflow.

[0069] In view of this, the present application provides an exhaust valve plate, which, by limiting the value of F1 / h and the lift height h, makes the elastic force F1 on the valve plate head and the lift height h satisfy: 1.5≤F1 / h≤2.2, 1.5≤h≤2.3, thereby optimizing the dynamic response characteristics of the valve plate opening and closing.

[0070] The structure of the exhaust valve plate 20 will be further explained below with reference to the attached drawings.

[0071] Please see Figure 3 and Figure 4 The exhaust valve plate 20 provided in this application embodiment includes a valve plate head 21, a valve plate tail 23, and a deformation section 22. The deformation section 22 is located between the valve plate head 21 and the valve plate tail 23, and connects the valve plate head 21 and the valve plate tail 23, providing elastic support for the movement of the valve plate head 21.

[0072] The tail portion 23 of the valve plate is configured to be connected to the cylinder head 10 of the cylinder. The head portion 21 of the valve plate is configured to be disposed opposite to the exhaust valve port 11 of the cylinder head 10 and is movable relative to the cylinder head 10, thereby opening or closing the exhaust valve port 11 during the compressor exhaust process.

[0073] The tail 23 of the valve plate is the part of the structure that connects the exhaust valve plate 20 to the cylinder head 10. The tail 23 of the valve plate can be fixedly installed on the cylinder head 10 by riveting, screwing, welding or other means to ensure that the exhaust valve plate 20 as a whole will not shift during operation, and to allow the valve plate head 21 and the deformation section 22 to move relative to the tail 23 of the valve plate to block or avoid the exhaust valve hole 11.

[0074] It can be understood that the valve head 21 is a partial structure provided by the exhaust valve plate 20 corresponding to the exhaust valve hole 11, which can completely block the exhaust valve hole 11, and its outer circumferential dimension can be slightly larger than the inner diameter dimension of the exhaust valve hole 11. This embodiment does not impose specific restrictions on the shape of the valve head 21, and the shape of the valve head 21 can be circular, fan-shaped, trapezoidal or other shapes.

[0075] Please see Figure 2 When the valve head 21 closes the exhaust valve port 11, the point corresponding to the center of the valve head 21 and the center of the exhaust valve port 11 is defined as the reference point Q. During the process of the valve head 21 moving relative to the cylinder head 10 to open the exhaust valve port 11, the reference point Q can be raised relative to the cylinder head 10 to a height equal to the lift height h.

[0076] Setting the reference point Q ensures that the measurement results of the lift height h are consistent and accurate under different scenarios, and provides a measurement basis for defining the relationship between the elastic force F1 and the lift height h.

[0077] The lift height h refers to the vertical distance by which the reference point Q of the exhaust valve plate 20 is raised during the process of moving relative to the cylinder head 10 from the closed exhaust valve port 11 to open the exhaust valve port 11. The lift height h reflects the amount of deformation of the valve plate during the opening process, that is, the opening range of the exhaust valve plate 20.

[0078] When the reference point Q is raised to the lift height h, the valve head 21 will be subjected to a spring force F1 due to its own elasticity. The unit of spring force F1 is N, and the unit of lift height h is mm.

[0079] The applicant found in the study that, at a certain lift height h, the elastic characteristics of the exhaust valve plate 20 affect the opening response speed and closing reliability of the exhaust valve plate 20, thereby affecting the dynamic response characteristics of the exhaust valve plate 20.

[0080] When h < 1.5 mm, for example, when h is 1.2 mm, the lift height of the exhaust valve plate 20 is insufficient, the exhaust flow area is limited, the resistance to high-pressure gas discharge increases, which can easily lead to increased compressor over-compression losses, decreased exhaust efficiency, and consequently reduced operating energy efficiency.

[0081] When h > 2.3 mm, for example, when h is 2.5 mm, the lift height of the exhaust valve plate 20 is too large, significantly increasing the bending stress of the exhaust valve plate 20. Under long-term high-frequency operation, the exhaust valve plate 20 is prone to fatigue cracks, and its fatigue life is greatly shortened. At the same time, an excessive lift height h can easily increase the impact of the exhaust valve plate 20 when it sits, increase the impact speed, significantly increase the impact noise, and may also damage exhaust components such as the valve seat and limit plate. In addition, an excessive lift height will also increase the risk of chattering during the valve plate opening and closing process, affecting the dynamic response stability and thus interfering with the normal operation of the compressor.

[0082] Therefore, in this embodiment, the lift height h of the exhaust valve plate 20 is limited to between 1.5 and 2.3 mm. For example, the lift height h can be 1.5 mm, 1.8 mm, 2.1 mm, 2.3 mm, etc.

[0083] Figure 6 A graph showing the relationship between compressor performance and the lift height h of the exhaust valve plate 20 is presented. Figure 7 A graph showing the relationship between compressor noise and the effective mass m of the exhaust valve plate 20 is presented. (See figure.) Figure 6 and Figure 7 As shown, this embodiment can improve the matching accuracy between the lift height h and the elastic force h by limiting the range of the lift height h, thereby further improving the dynamic response characteristics, operational reliability and adaptability of the exhaust valve plate 20, which helps to reduce the noise of the compressor or improve the energy efficiency of the compressor.

[0084] Within the aforementioned range, the lift height h ensures sufficient exhaust flow area when the exhaust valve plate 20 opens the exhaust valve orifice 11, effectively reducing gas discharge resistance, minimizing over-compression losses, and improving compressor exhaust efficiency and energy efficiency. Simultaneously, within this range, the bending stress of the exhaust valve plate 20 is moderate, effectively avoiding fatigue life reduction caused by excessive lift. The seating impact is also within a controllable range, helping to reduce the impact noise between the exhaust valve plate 20 and the cylinder head 10 during the return process.

[0085] Meanwhile, the value of F1 / h is one of the parameters characterizing the dynamic response characteristics of the valve plate, which can affect the ease of opening the exhaust valve plate 20 and its response speed to exhaust pressure. The rationality of the value of F1 / h directly affects the operating efficiency and noise level of the compressor. The lift height h characterizes the amount of working deformation of the valve plate during the opening process, and its value is directly related to the bending stress of the valve plate, the exhaust flow area, and the impact strength of the seat.

[0086] In this embodiment, when the reference point Q is raised to the lift height h, the elastic force F1 on the valve head 21 and the lift height h satisfy the following relationship: 1.5 ≤ F1 / h ≤ 2.2. For example, the value of F1 / h can be 1.5, 1.8, 2.1, 2.2, etc.

[0087] When F1 / h is less than 1.5, for example, when F1 / h is 1.2, the stiffness of the exhaust valve plate 20 is too low, resulting in a slow response rate to exhaust pressure. Although it can open at lower exhaust pressures, the closing process is prone to delays, leading to increased high-pressure gas backflow losses. This, in turn, causes a decrease in compressor cooling capacity, an increase in power consumption, and ultimately reduces operating efficiency. Simultaneously, low stiffness increases the impact force during valve plate opening and closing, raising the impact speed and exacerbating the impact wear between the exhaust valve plate 20 and the valve seat and limit plate, generating significant impact noise. Long-term high-frequency operation can easily lead to fatigue damage to the valve plate, shortening its service life.

[0088] When F1 / h = 1.5, compared to when F1 / h is less than 1.5, the stiffness of the exhaust valve plate 20 is improved, balancing the flexibility of valve plate opening and the timeliness of closing. The response rate to exhaust pressure basically meets the requirements of conventional compressor operating conditions. At this time, the exhaust valve plate 20 can open quickly under reasonable exhaust pressure and helps to avoid significant closing delay and reduce backflow losses.

[0089] When F1 / h > 2.2, for example, when F1 / h is 2.5, the stiffness of the exhaust valve plate 20 is too high, and the opening resistance of the exhaust valve plate 20 increases significantly. Higher exhaust pressure is required to open the valve plate, resulting in delayed valve opening, decreased compressor exhaust efficiency, reduced cooling capacity, increased power consumption, and thus reduced operating energy efficiency. At the same time, excessively high stiffness of the exhaust valve plate 20 will aggravate the rigid impact during the opening and closing process of the exhaust valve plate 20, further increasing the impact noise and affecting the operating comfort of the compressor. Long-term high-frequency impact may also cause wear on exhaust components such as valve seat and limit plate, increasing equipment maintenance costs.

[0090] When F1 / h = 2.2, compared to F1 / h > 2.2, the stiffness of the exhaust valve plate 20 is reduced, providing sufficient elastic restoring force to ensure timely valve closure and avoid backflow loss. Simultaneously, the reduced stiffness of the exhaust valve plate 20 at this time will not result in excessive opening resistance, allowing for normal opening under normal exhaust pressure, thus adapting to high exhaust pressure and demanding timely valve closure conditions.

[0091] When 1.5 < F1 / h < 2.2, for example, when F1 / h is 1.8, the stiffness of the exhaust valve plate 20 can coordinate the elastic characteristics of the exhaust valve plate 20 with the pressure pulsation during the compressor exhaust process. This ensures that the valve plate responds quickly to the exhaust pressure and opens in time, and also ensures that it closes quickly after exhaust, minimizing high-pressure gas backflow loss and impact noise. At the same time, the exhaust valve plate 20 can reduce the valve plate opening and closing impact force and reduce the impact speed, thus achieving both energy efficiency improvement and noise reduction.

[0092] Therefore, in this embodiment, the value of F1 / h is limited to the range of 1.5 to 2.2, which enables the elastic characteristics of the valve plate to be coordinated with the pressure pulsation during the compressor discharge process. This ensures that the discharge valve plate 20 responds quickly to the action of the compressor discharge pressure pulsation, which helps to avoid poor discharge and over-compression loss caused by delayed opening. At the same time, it also helps to ensure that the discharge valve plate 20 closes in time after the discharge is completed, reducing the phenomenon of high-pressure gas backflow. This improves the dynamic response characteristics of the discharge valve plate 20 and adapts to the needs of high-frequency operation of the compressor.

[0093] In summary, this embodiment limits the value of F1 / h and the lift height h, ensuring that the elastic force F1 and lift height h on the valve head 21 satisfy: 1.5≤F1 / h≤2.2, 1.5≤h≤2.3. This optimizes the dynamic response characteristics of the valve opening and closing, ensuring rapid opening and timely closing of the valve, reducing backflow loss and impact noise, controlling the bending stress of the valve, extending fatigue life, improving the performance of the compressor unit, and reducing the operating noise of the compressor. As a result, the exhaust valve 20 can be used with compressors with a cooling capacity of 2500W-3700W and covers most conventional operating conditions.

[0094] The exhaust valve plate 20 also includes a deformation section 22, which is located between the valve plate head 21 and the valve plate tail 23 to connect the valve plate head 21 and the valve plate tail 23.

[0095] Please see Figure 3 and Figure 4 In some embodiments, with the center of the exhaust valve hole 11 as the central axis, the average diameter corresponding to each differential circular arc segment in the valve head 21 is taken as the diameter of the valve head 21 as d1, the average width of the deformation segment 22 is W1, and the length of the deformation segment 22 is L1.

[0096] The outline of the valve head 21 can be composed of continuous arcs, such as a circular or fan-shaped structure. The outline of the valve head 21 is decomposed into countless tiny arc segments, each corresponding to its own diameter. The arithmetic mean of the diameters of all these arc segments is then calculated; this mean can be the diameter d1 of the valve head 21. Obtaining the diameter d1 of the valve head 21 in this way helps ensure the accuracy of the subsequent formula for calculating the elastic force F.

[0097] The valve head 21, deformation section 22, and valve tail 23 are arranged along the length of the exhaust valve 20. The total length of the exhaust valve 20 is L2, and the thickness of the exhaust valve 20 is t. The units of d1, W1, L1, L2, and t are all mm. The parameters of the exhaust valve 20 satisfy the following condition:

[0098]

[0099] Where E is the elastic modulus of the material of the exhaust valve plate 20, in GPa; k is the first correction coefficient, and S is the shape coefficient. k and S are determined according to the structure of the valve plate head 21. The structure of the valve plate head 21 includes a fan-shaped structure, a circular structure, or a first shape structure. The first shape structure includes other shape structures besides the fan-shaped structure and the circular structure.

[0100] The conditional expressions satisfied by the parameters of the exhaust valve plate 20 can be used to determine the range of theoretical elastic force values ​​experienced by the valve plate head 21. During the design phase of the exhaust valve plate 20, based on the selected valve plate head 21 structure, elastic modulus E, and various geometric parameters, the corresponding first correction coefficient k and shape coefficient S are determined. Substituting these into the above formula, the theoretical elastic force value experienced by the valve plate head 21 when the reference point Q is raised to the lift height h can be calculated.

[0101] It should be noted that, due to the differences in the force characteristics and deformation patterns of valve head 21 with different shapes, the fan-shaped structure, circular structure, and first shape structure correspond to different k, and the fan-shaped structure, circular structure, and first shape structure correspond to different S. Among them, the first shape structure can be other shapes such as trapezoidal, rectangular, and rhomboid.

[0102] The theoretical value is compared with the range of F1 / h and h values ​​defined in the embodiments of this application. If the theoretical value is within the range, it can be preliminarily determined that the design scheme meets the stiffness requirements. If the theoretical value exceeds the range, the geometric parameters or material properties can be adjusted, and the calculation and verification can be repeated until the theoretical value meets the requirements. Then, experimental measurement and verification can be carried out, thereby shortening the design cycle and reducing the experimental cost.

[0103] It is understood that the above conditional expression describes the theoretical elastic force value and its range for the exhaust valve plate 20 at the lift height h. This theoretical elastic force value can be used for theoretical verification of the actual elastic force value, but it cannot completely replace the aforementioned standardized test measurement method. The theoretical elastic force value can serve as a design reference and optimization basis; combining the two can further improve the reliability of the exhaust valve plate 20 stiffness design.

[0104] Figure 8 The graph shows the relationship between compressor performance and the elastic force F1 of the exhaust valve plate 20. Figure 9 A graph showing the relationship between compressor noise and the spring force F1 of the exhaust valve plate 20 is presented. Figure 8 and Figure 9 As shown, in this embodiment, the value of F1 is limited to 2.7~4.2, ensuring that the value of F1 / h is within the limited range of 1.5~2.2N / mm, thereby ensuring the coordinated adaptation of the valve plate dynamic characteristics and the compressor exhaust pressure pulsation, and achieving the technical effects of improved energy efficiency and reduced noise.

[0105] In some embodiments, when the structure of the valve head 21 is a fan-shaped structure, k=32 and S=1.1.

[0106] Among them, the first correction coefficient k is mainly used to correct the influence of the uneven stress on the stiffness calculation of the sector structure, while the shape coefficient S is used to adapt to the contour characteristics of the sector structure, compensate for the deformation difference between its edge region and center region, and ensure that the theoretical calculation can accurately reflect the actual stiffness characteristics of the sector structure valve plate.

[0107] It should be noted that k=32 and S=1.1 are applicable to the case where the valve head 21 is a fan-shaped structure, and the fan-shaped structure corresponding to these values ​​must meet the conventional design size range. If the size of the fan-shaped structure exceeds the conventional range, the values ​​of the first correction coefficient k and the shape coefficient S can be adjusted according to the actual structure to ensure the accuracy of the theoretical calculation.

[0108] Please see Figure 3 In some embodiments, the fan-shaped structure has two intersecting first sides 211, both of which are circular arc edges with a radius of R1. The included angle between the two first sides 211 is α, where 15°≤α≤75° and 60mm≤R1≤100mm.

[0109] For example, the included angle α between the two first sides 211 can be 15°, 25°, 35°, 45°, 55°, 65°, 75°, etc. The radius R1 of the first side 211 can be 60mm, 70mm, 80mm, 90mm, 100mm, etc.

[0110] It should be noted that the fan-shaped structure can be a structure similar to a fan shape. In this embodiment, the first side 211 can be arc-shaped, and the first side 211 can bulge outward toward the outside of the valve head 21. The first side 211 is the arc-shaped edge connecting the valve head 21 and the deformation section 22. The contours of the two connecting arc edges can be flexibly designed according to the transition requirements between the valve head 21 and the deformation section 22.

[0111] The deformation section 22 and the valve head 21 can be transitioned through the first side 211 of the fan-shaped structure. The arc-shaped contour allows the thickness and stress area of ​​the valve head 21 to present a gradual distribution, which helps to ensure a uniform stiffness distribution of the fan-shaped head, rather than an abrupt distribution, thereby helping to avoid stress concentration caused by local stiffness abrupt changes. In this way, during the opening and closing of the exhaust valve 20, the deformation section 22 and the valve head 21 can produce relatively uniform deformation, which helps to avoid fatigue damage caused by excessive local deformation.

[0112] The included angle α between the two first side edges 211 can be the included angle formed between the tangents of the two first side edges 211 near the end of the deformed segment 22. Its size will determine the outline shape, coverage area, width of the transition area and stiffness distribution of the fan-shaped head. Different values ​​will also affect the performance of the valve plate.

[0113] When the included angle α is less than 15°, for example, when the included angle α is 12°, the included angle α is too small, and the included angle between the two first sides 211 of the sector structure is closer to parallel. At this time, the area of ​​the valve head 21 is too large, which can easily lead to the sector head covering too wide a range, which will increase the mass of the sector head, affect the timeliness of valve closing, increase the probability of gas backflow and impact noise, and reduce the compressor energy efficiency.

[0114] When α equals 15°, it is at the lower limit of the defined range. The coverage area of ​​the fan-shaped head can basically meet the sealing requirements of the small exhaust valve orifice 11. At the same time, the width of the transition area is moderate, and the stress can be basically evenly distributed along the arc edge, ensuring the connection strength between the deformation section 22 and the valve head 21. Compared with the case where α is less than 15°, the deformation of the valve during the opening and closing process is smoother, which can effectively reduce fatigue damage. At the same time, it can be combined with the aforementioned design of the lift height h and F1 / h ratio to better maintain the stability of the valve's dynamic response.

[0115] When α is greater than 75°, for example, when the included angle α is 80°, the included angle between the two first sides 211 is too large. In this case, the area of ​​the valve head 21 is relatively small, which may make it difficult to completely cover the exhaust valve hole 11. High-pressure gas may leak from the uncovered area, thereby reducing the compressor's exhaust efficiency. At the same time, a large included angle may also make the stiffness distribution of the valve head 21 uneven. The stiffness near the edge area may be significantly lower, and excessive local deformation may occur during the opening and closing of the valve. Long-term operation may lead to local fatigue damage, affecting the service life of the valve.

[0116] When α equals 75°, the coverage area of ​​the sector head reaches a large value, which can meet the sealing requirements of the large exhaust valve orifice 11 and adapt to the exhaust flow requirements of the large displacement compressor. Compared with the case where α is greater than 75°, it helps to avoid excessive mass of the sector head, and the valve plate is less likely to have excessive inertia during opening and closing, resulting in response lag. At the same time, it can better maintain the stability of the F1 / h ratio, taking into account both sealing performance and dynamic response characteristics.

[0117] In this embodiment, when the included angle α is limited to between 15° and 75°, for example, when the included angle α is 45°, the effective coverage area of ​​the valve plate head 21 has good compatibility with the stress of the transition area. This ensures that the exhaust valve hole 11 is completely covered by a reasonable coverage area, meeting the sealing requirements of exhaust valves of different specifications. Simultaneously, the width of the transition area is moderate, and the stress is evenly distributed along the arc edge, thus helping to avoid stress concentration. At the same time, α within this range allows for a reasonable mass distribution of the fan-shaped head, which helps ensure that the F1 / h ratio remains stable within the range of 1.5 to 2.2. This allows for a better and faster response to exhaust pressure pulsations to open the valve, and also enables timely closing to reduce backflow loss and impact noise.

[0118] The radius R1 of the arc edge determines the smoothness of the transition area between the two first sides 211 of the valve head 21, affecting the stress transmission efficiency and connection strength.

[0119] When R1 is less than 60mm, for example, when R1 is 55mm, the curvature of the arc edge is too large, the transition area is too steep, and the connection between the deformation section 22 and the valve head 21 is prone to show a more obvious angle shape. The stress generated during the opening and closing of the valve is difficult to be evenly distributed along the arc edge and tends to accumulate at the transition connection, which may aggravate stress concentration. Under long-term high-frequency alternating load, the probability of fatigue cracks appearing at the connection will increase, which may lead to valve breakage and chatter.

[0120] When R1 equals 60mm, the curvature of the arc edge is moderate, which can effectively disperse stress. At the same time, the arc edge can ensure the connection strength between the deformation section 22 and the valve head 21. During the opening and closing of the valve, the stress is smoothly transferred from the valve head 21 to the deformation section 22, and stress accumulation is not likely to occur.

[0121] When R1 is greater than 100mm, for example, when R1 is 105mm, the curvature of the arc edge is too small, which results in the length of the transition area connecting the valve head 21 and the deformation section 22 being too long. This may increase the overall mass of the valve and thus disrupt the balance of the F1 / h ratio, affecting the dynamic response speed of the valve and causing a response lag.

[0122] When R1 equals 100mm, the curvature of the arc edge is relatively small, the transition area is smooth and gentle, and the stress dispersion effect is good, which can further reduce the risk of stress concentration. At the same time, the length of the transition area is moderate, which will not affect the effective force-bearing area of ​​the valve plate, and can ensure the connection strength between the deformation section 22 and the valve plate head 21, and ensure the coverage area of ​​the fan-shaped head.

[0123] In this embodiment, when the radius R1 of the first side 211 is between 60mm and 100mm, for example, when R1 is 85mm, the transition area where the arc edge is located is smooth and gentle. The stress generated during the opening and closing of the valve plate can be evenly distributed along the arc edge, effectively avoiding stress concentration. At the same time, the length of the transition area is moderate, neither too short leading to insufficient connection strength nor too long leading to a reduction in the effective force-bearing area, thus balancing connection strength and effective force requirements. R1 within this range can work in conjunction with α between 15° and 75° to ensure uniform stiffness distribution of the fan-shaped head, which helps to ensure that the lift height is within the range of 1.5 to 2.3, resulting in stable dynamic response of the valve plate and adaptability to compressor operating conditions with different displacements and speeds, thereby significantly improving the reliability and adaptability of the valve plate.

[0124] In summary, this embodiment limits R1 to 60~100mm and the included angle α between the two first sides 211 of the valve head 21 to 15°~75°, which can effectively improve the operational stability of the exhaust valve 20. Under the condition of rapid opening and closing of the exhaust valve 20, the arc transition area between the deformation section 22 and the valve head 21 can effectively disperse the stress generated by the alternating load, reduce the generation of fatigue cracks, reduce the risk of valve root fracture and chatter, and extend the service life of the exhaust valve 20. At the same time, the uniform stiffness distribution can make the dynamic response of the valve head 21 more stable, which helps to avoid opening and closing jamming or delay caused by uneven local stiffness, further ensuring that the valve opens quickly and closes in time, reducing high-pressure gas backflow loss and impact noise, and helping to improve the energy efficiency of the compressor.

[0125] In some embodiments, when the structure of the valve head 21 is circular, k=25 and S=0.9.

[0126] Because the circular valve head 21 differs in shape from the aforementioned fan-shaped structure, there is a difference between the first correction factor and the shape factor. The first correction factor k is primarily used to correct the influence of the circular structure on stiffness calculations and compensate for the stress transfer differences between the circular head and the transition region of the deformation segment 22. The shape factor S is used to adapt to the contour characteristics of the circular structure, correct the correlation between the area of ​​the circular head and the stress efficiency, and ensure that theoretical calculations accurately reflect the actual stiffness characteristics of the circular exhaust valve 20, providing a reliable basis for stiffness prediction during the design phase.

[0127] Please see Figure 4 In some embodiments, the circular structure has two opposing second sides 212 on the side facing the deformation segment 22. Both second sides 212 are arc edges with a radius of R2, where R2 is in mm. R2 and d1 satisfy the following relationship: 0.05≤R2 / d1≤2.5.

[0128] For example, the value of R2 / d1 can be 0.05, 0.3, 0.9, 1.0, 1.25, 1.5, 1.75, 2.0, 2.25, 2.5, etc.

[0129] Two opposing second sides 212 serve as the direct connection points between the circular valve head 21 and the deformation section 22, achieving a smooth connection between the circular head and the deformation section 22. Similar to the first side 211 of the aforementioned fan-shaped structure, the second side 212 is designed as an arc edge, which can effectively disperse the alternating stress generated during the opening and closing of the valve. Compared with right-angle transitions or other irregular transition forms, the arc edge transition allows stress to be smoothly transferred from the circular head to the deformation section 22, reducing stress accumulation at the connection point, lowering the risk of fatigue cracks and fractures in the transition area, and improving the long-term operational reliability of the valve.

[0130] The ratio of R2 / d1 was determined by the applicant based on the outline dimensions, stress characteristics, and practical application experience of the circular structure, in order to achieve the adaptation of the transition structure to the size of the circular head and ensure a balance between the transition effect and the structural strength.

[0131] When R2 / d1 is less than 0.05, for example, R2 / d1=0.04, R2 is too small relative to d1. The curvature of the second side 212 is large, making the transition area between the valve head 21 and the deformation section 22 too steep. The connection between the circular head and the deformation section 22 shows a more obvious sharp bend. The stress is difficult to be evenly distributed along the arc edge and tends to accumulate at the connection, which may aggravate stress concentration. Under long-term high-frequency alternating load, the probability of fatigue cracks appearing at the connection will increase, which may affect the structural stability of the exhaust valve 20.

[0132] When R2 / d1 is greater than 2.5, for example, R2 / d1=2.8, R2 is too large relative to d1, the curvature of the second side 212 is too small, the transition area is too gentle, resulting in an excessively long transition area. This may increase the overall mass of the valve plate, increasing the total mass of the valve plate head 21 and the deformation section 22 of the exhaust valve plate 20. This may disrupt the balance of the F1 / h ratio, affecting the dynamic response speed of the valve plate and causing a response lag.

[0133] Limiting the value of R2 / d1 to 0.05~2.5 ensures a smooth transition between the circular head and the deformation section 22, resulting in a more uniform stiffness distribution in the valve head 21 and reducing the impact of abrupt stiffness changes on theoretical calculations. Simultaneously, the smooth transition structure reduces stress concentration, lowers the risk of valve fatigue failure, and extends valve life. Combined with the limitation on the ratio of lift height h to F1 / h, this further ensures that the dynamic characteristics of the valve are coordinated with the compressor's discharge pressure pulsation, achieving the technical effects of improved energy efficiency and reduced noise.

[0134] Therefore, this embodiment achieves a smooth transition between the circular head and the deformation section 22 by setting two opposing arc-shaped second sides 212 with a radius of R2 on the side of the circular valve head 21 facing the deformation section 22, and limiting the value of R2 / d1 to 0.05~2.5. This optimizes the stress transmission path, effectively avoids stress concentration, and takes into account structural strength, effective force-bearing area and overall valve size. Combined with the aforementioned k, S values ​​and stiffness parameter limitations, the design of the circular exhaust valve 20 is further improved, enhancing its operational reliability, dynamic response characteristics and adaptability. It can better meet the exhaust requirements of compressors of different specifications and provide strong support for the efficient and low-noise operation of the compressor.

[0135] In some embodiments, when the structure of the valve head 21 is a first shape, k=30 and S=1.0, so as to facilitate theoretical calculation of the elastic force F1 of the exhaust valve 20 with other shapes.

[0136] In some embodiments, the exhaust valve plate 20 is disposed on a compressor including a cylinder, and the compressor operates at an operating frequency of 120 Hz and an exhaust pressure of 2.93 MPa, and d1, W1, L1, L2 and t satisfy the following conditional expression:

[0137]

[0138] Where ρ is the material density of the exhaust valve plate 20, in g / cm³, and e is the natural constant, taken as 2.718.

[0139] It should be noted that the above conditional expression reflects the dynamic response characteristics of the compressor. Among them, It can reflect the exhaust flow capacity when the exhaust valve plate is open. It can reflect the elastic recovery capability of the exhaust valve plate 20, and affect the reset speed and stability of the valve plate when it is closed.

[0140] In this embodiment, the geometric parameters and material parameters of the exhaust valve plate 20 are coupled with the compressor operating parameters to establish a parameter constraint relationship under specific high-frequency and high-pressure conditions. This constraint relationship serves as a theoretical calculation reference, and its core function is to provide precise theoretical guidance and quantitative basis for the parameter design of the exhaust valve plate 20. This relationship couples the valve plate's geometric parameters, material parameters, and operating parameters to comprehensively regulate the valve plate's exhaust flow capacity and elastic recovery capacity, ensuring that the valve plate can both smoothly exhaust and quickly settle under 120Hz and 2.93MPa operating conditions, effectively avoiding adverse phenomena such as flutter and delayed closure. At the same time, fine-tuning the parameters based on actual engineering test data can further improve the valve plate's performance adaptability.

[0141] When the values ​​obtained based on the above parameters and conditions are between 20 and 30, the exhaust valve plate's exhaust flow capacity and elastic recovery capacity are matched, making it suitable for high-frequency, high-pressure conditions of 120Hz and 2.93MPa. At this time, when the exhaust valve plate 20 is open, the exhaust flow is smooth, effectively reducing gas discharge resistance, lowering over-compression losses, and ensuring compressor exhaust efficiency. When the exhaust valve plate 20 is closed, its elastic recovery is rapid, allowing it to settle promptly, helping to avoid delayed closing and chattering phenomena, reducing backflow losses and impact noise, while ensuring that the valve plate's bending stress is within a controllable range, extending fatigue life. This value range is the optimal interval obtained by fitting a large amount of experimental data, maximizing the dynamic response characteristics of the valve plate and achieving high-efficiency, low-noise compressor operation.

[0142] It should be noted that the above constraint relationship applies to the rated high-frequency, high-pressure operating conditions of the compressor at a 120Hz operating frequency and a 2.93MPa discharge pressure. If the compressor's operating conditions fluctuate (such as changes in operating frequency or discharge pressure), the geometric parameters can be fine-tuned by adjusting the value of the correction coefficient k, or by combining it with the parameter limits mentioned above, to ensure that the overall value of the constraint relationship remains within a reasonable range of 20-30, thus achieving operating condition adaptation. At the same time, the values ​​of each parameter in the formula must adhere to the previously defined range to ensure parameter synergy and avoid the constraint relationship being unsatisfied due to deviations in a single parameter, thereby affecting the performance of the discharge valve plate 20 and the compressor.

[0143] Please see Figure 3 and Figure 4 In some embodiments, L1 and L2 satisfy the following relationship: 0.3≤L1 / L2≤0.5.

[0144] For example, L1 / L2 can be 0.3, 0.35, 0.4, 0.45, 0.5, etc.

[0145] L1 / L2 reflects the proportion of the deformable section 22 in the length of the exhaust valve plate 20. The ratio of L1 / L2 directly affects the stress characteristics, stiffness distribution, and dynamic motion state of the valve plate.

[0146] When L1 / L2 is less than 0.3, for example, L1 / L2 = 0.25, the proportion of L1 in L2 is too small, and the length of the deformation section 22 is insufficient. This restricts the elastic deformation space of the exhaust valve plate 20, causing deformation to easily concentrate at the root of the connection between the deformation section 22 and the tail 23 of the valve plate. This results in an extremely high stress concentration factor at the root. Under long-term high-frequency alternating loads, fatigue cracks are prone to appear at the root, which may lead to valve plate root fracture and affect the service life of the valve plate. At the same time, an excessively short deformation section 22 will increase the stiffness of the exhaust valve plate 20, which may lead to excessive valve plate opening resistance, lag in dynamic response, and an inability to well adapt to the needs of compressor exhaust pressure pulsation.

[0147] When L1 / L2 equals 0.3, compared to L1 / L2=0.25, the overall structure of the exhaust valve plate 20 balances a certain elastic deformation capacity and structural rigidity. The length of the deformation section 22 can basically meet the elastic stroke required for the valve plate to open and close. The deformation is no longer excessively concentrated at the root, and the stress concentration coefficient is within a controllable range, which can effectively reduce the risk of root fracture.

[0148] When L1 / L2 is greater than 0.5, for example, L1 / L2=0.55, the proportion of L1 in L2 is too large, and the deformation section 22 is too long. This leads to a decrease in the overall stiffness of the valve plate, which can easily result in insufficient elastic reset capability when the valve plate closes, delayed closing, increased high-pressure gas backflow loss, and impact noise. At the same time, the excessively long deformation section 22 is prone to bending fluctuations during high-speed opening and closing, causing unstable valve plate movement and significantly increasing the risk of chatter.

[0149] When L1 / L2 equals 0.5, the deformation section 22 is relatively long, and the exhaust valve plate 20 has a strong elastic deformation capacity and sufficient elastic stroke, facilitating flexible adjustment of stiffness and better adapting to the needs of different exhaust pressure pulsations. Simultaneously, the fixed end of the valve plate retains sufficient length to ensure installation reliability, relatively uniform stress distribution, and a low risk of stress concentration, meeting the operating conditions of compressors requiring large elastic deformation. Compared to the case where L1 / L2 is greater than 0.5, this helps avoid excessive reduction in the overall stiffness of the exhaust valve plate 20 due to an excessively long deformation section 22, while also reducing the risk of bending fluctuations and chattering during high-speed opening and closing, maintaining the stability of the valve plate's dynamic movement.

[0150] In this embodiment, when the value of L1 / L2 is limited to between 0.3 and 0.5, for example, L1 / L2 = 0.4, the proportion of the deformation section 22 in the exhaust valve plate 20 achieves the optimal balance between the valve plate's elastic stroke, structural strength, and dynamic stability. On one hand, the sufficient length of the deformation section 22 ensures that the valve plate has enough elastic stroke, facilitating good stiffness adjustment and ensuring that the exhaust valve plate 20 responds quickly to opening and closing. On the other hand, the length of the deformation section 22 within this proportional range is not excessive, preventing the exhaust valve plate 20 from bending and fluctuating during high-speed opening and closing, ensuring stable movement of the exhaust valve plate 20, reducing the risk of chatter, and adapting to the high-frequency operating conditions of most compressors. In addition, the tail 23 of the valve plate retains sufficient length and strength to ensure reliable installation, avoiding abnormal valve plate movement caused by loose installation; at the same time, stress can be evenly distributed along the deformation section 22, effectively reducing the stress concentration factor, reducing fatigue damage, and improving the fatigue life of the valve plate.

[0151] In summary, by limiting the ratio of L1 to L2 to a range of 0.3 to 0.5, this embodiment of the application can effectively balance the elastic stroke, structural strength, and dynamic stability of the exhaust valve plate 20. This ensures that the exhaust valve plate 20 has sufficient elastic stroke to achieve good stiffness adjustment, while also ensuring that the fixed end has sufficient strength for reliable installation, resulting in a more uniform stress distribution and thus improving the fatigue life of the valve plate. At the same time, it helps to avoid problems such as abnormal stiffness and unstable movement. Combined with the aforementioned parameter design, the overall design of the exhaust valve plate 20 is further improved, enhancing its operational reliability, dynamic response characteristics, and adaptability, providing strong support for the efficient and low-noise operation of the compressor.

[0152] To further optimize the geometric adaptability of the exhaust valve plate 20, the proportional relationship between the length L1 of the deformed section 22 and the diameter d1 of the valve plate head 21 is limited.

[0153] Please see Figure 3 and Figure 4 In some embodiments, L1 and d1 satisfy the following relationship: 0.7≤L1 / d1≤1.4.

[0154] For example, the value of L1 / d1 can be 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, etc.

[0155] L1, representing the dimension of the deformation section 22, affects the elastic deformation capacity and stiffness level of the valve disc. d1, representing the dimension of the valve disc head 21, affects the coverage area, mass distribution, and sealing performance of the valve disc head 21. The ratio between the length L1 of the deformation section 22 and the diameter d1 of the valve disc head 21 directly relates to the dimensional matching degree between the valve disc head 21 and the deformation section 22, thus affecting the stability of the elastic force F1 value and the F1 / h ratio, and also relating to the sealing reliability and impact characteristics of the valve disc.

[0156] When L1 / d1 is less than 0.7, for example, L1 / d1 = 0.6, L1 is relatively small compared to d1. This means that the valve head 21 is larger and heavier than the deformation section 22, significantly increasing the mass proportion of the valve head 21. This leads to an increase in the combined mass of the valve head 21 and the deformation section 22. Even with stiffness adjustments, this can cause a delay in the closing of the exhaust valve 20, increasing high-pressure gas backflow losses and impact noise. Furthermore, an excessively large valve head 21 increases the rotational inertia of the head. During valve opening and closing, the impact torque on the cylinder head 10 also increases accordingly. Long-term high-frequency impacts can not only exacerbate cylinder head 10 wear but may also cause fatigue damage to the valve head 21, affecting the service life of the exhaust valve 20.

[0157] When L1 / d1 equals 0.7, for example, L1 / d1=0.7, compared to L1 / d1 being less than 0.7, the dimensions of the valve head 21 and the deformation section 22 are basically matched, and the mass ratio of the valve head 21 is within a reasonable range, which helps to avoid the problem of closing delay. At the same time, the rotational inertia of the valve head 21 is within a controllable range, which can effectively reduce the wear of the cylinder head 10 and the fatigue damage of the exhaust valve 20.

[0158] When L1 / d1 is greater than 1.4, for example, L1 / d1=1.5, L1 is relatively large relative to d1, which means that the head of the exhaust valve plate 20 is relatively small. The head size may not be able to completely cover the exhaust valve hole 11, which can easily lead to sealing leakage. High-pressure gas will leak from the uncovered area, which will reduce the exhaust efficiency of the compressor, aggravate gas backflow, and increase energy consumption and noise. At the same time, the problem of reduced stiffness caused by the excessive length of the deformation section 22 will become more prominent, which may lead to insufficient elastic reset ability when the valve plate is closed, unstable dynamic response, and increased risk of chatter. In addition, if the proportion of the valve plate head 21 is too small, it may also lead to insufficient head mass, reduced fit with the valve seat, and further aggravate the risk of sealing failure.

[0159] When L1 / d1 equals 1.4, the length of the deformation section 22 and the diameter of the valve head 21 are well matched, resulting in sufficient elastic deformation capacity of the deformation section 22. This allows for better adjustment of the elastic force F1, ensuring that F1 and h change synchronously according to a predetermined ratio and maintaining the stability of the F1 / h ratio. At the same time, the coverage area of ​​the valve head 21 can still meet the sealing requirements of the conventional exhaust valve hole 11, making it less prone to significant leakage problems. Compared to the case where L1 / d1 is greater than 1.4, this effectively avoids sealing failure caused by an excessively small proportion of the valve head 21, while also mitigating the stiffness reduction problem caused by an excessively long deformation section 22, ensuring the structural rigidity and dynamic stability of the valve.

[0160] When L1 / d1 is between 0.7 and 1.4, for example, L1 / d1 = 1.1, the ratio of L1 to d1 is within an optimal range, achieving the best dimensional match between the deformation section 22 and the valve head 21. This ensures that F1 and h change synchronously according to a predetermined proportional relationship, thus stably achieving the design range of F1 / h. On one hand, the mass distribution of the valve head 21 and the deformation section 22 is reasonable, and the elastic deformation capacity of the deformation section 22 matches the stiffness requirements of the valve head 21, helping to keep the stiffness F1 / h within the range of 1.5 to 2.2. This ensures the valve opens quickly and closes promptly, reducing backflow loss and impact noise. On the other hand, the coverage area of ​​the valve head 21 is sufficient to completely cover and seal the exhaust valve hole 11, preventing leakage. Simultaneously, the length of the deformation section 22 is moderate, preventing a significant decrease in stiffness. In addition, the rotational inertia of the valve plate head 21 is moderate, and the impact torque on the cylinder head 10 is within a reasonable range, which can effectively extend the service life of the valve plate and valve seat, adapt to the high-frequency and conventional displacement conditions of most compressors, and take into account sealing performance, dynamic response characteristics and structural stability.

[0161] Furthermore, the L1 / d1 ratio limit can work synergistically with the aforementioned design parameters. A reasonable L1 / d1 ratio can ensure that the dimensions of the deformation section 22 and the valve head 21 are matched, so that the elastic force F1 on the valve head 21 changes synchronously with the lift height h, avoiding abnormal F1 / h ratio caused by asynchronous changes between the two, thereby ensuring the dynamic response characteristics of the valve.

[0162] At the same time, this ratio limit can take into account both sealing performance and stiffness stability, avoiding both an increase in impact torque caused by an excessively large valve plate head 21 and a sealing failure caused by an excessively small valve plate head 21. Combined with the ratio limit of L1 / L2, the overall structural dimensions of the valve plate can be further optimized, making the stress distribution more uniform, reducing fatigue damage, and improving the fatigue life of the exhaust valve plate 20.

[0163] Furthermore, this proportional limitation can be adapted to the theoretical calculation formula of elastic force F1, providing a clear basis for parameter optimization in the design stage, shortening the design cycle and reducing test costs.

[0164] It should be noted that the specific values ​​of L1 and d1 need to be determined in combination with the overall design dimensions of the valve plate, the specifications of the exhaust valve orifice 11, and the operating requirements of the compressor, to ensure that L1 / d1 is within the range of 0.7 to 1.4. At the same time, in conjunction with parameters such as L1 / L2, valve plate thickness t, and average width W1 of the deformation section 22, various performance parameters can be optimized in a coordinated manner.

[0165] Please see Figure 3 and Figure 4 In some embodiments, the average width of the valve tail 23 is W2, and W2 and the average width W1 of the deformed segment 22 satisfy the following condition: 0.2≤W1 / W2≤0.8.

[0166] For example, the values ​​of W1 / W2 can be 0.2, 0.3, 0.6, 0.8, etc.

[0167] The valve tail 23 serves as the fixed end of the valve plate, and its average width W2 determines the structural strength and installation reliability of the fixed end. The average width W1 of the deformation section 22 determines the elastic deformation capacity and stiffness level of the deformation section 22. The width ratio between the valve tail 23 and the deformation section 22 directly affects the smoothness of the width transition at the connection between the valve tail 23 and the deformation section 22, thereby affecting the stress distribution in this area.

[0168] When W1 / W2 is less than 0.2, for example, W1 / W2 = 0.15, W1 is relatively small compared to W2. This means that the deformation section 22 narrows too quickly relative to the tail 23 of the valve plate, resulting in a sudden change in the width from the tail 23 to the deformation section 22. This sudden change causes the stress at the bend of the tail 23 to not be smoothly dispersed, leading to strong stress concentration at the bend and increasing the stress concentration factor. Under long-term high-frequency cyclic loading, fatigue cracks are prone to appear at the connection between the deformation section 22 and the tail 23 of the exhaust valve plate 20. Gradually, these cracks may lead to valve plate fracture, significantly increasing the risk of fatigue failure and affecting the service life of the valve plate. Furthermore, an excessively narrow deformation section 22 may also result in insufficient structural strength, making the valve plate prone to abnormal deformation during rapid opening and closing, failing to stably provide a suitable stiffness K, and affecting the dynamic response characteristics of the valve plate.

[0169] When W1 / W2 equals 0.2, compared to when W1 / W2 is less than 0.2, the connection between the tail 23 of the valve plate and the deformation section 22 is smoother, reducing the risk of stress concentration at the connection and effectively lowering the probability of fatigue failure. At the same time, the deformation section 22 has a moderate width, providing a certain degree of flexibility, which helps ensure that the valve plate head 21 has a suitable elastic force F1, avoiding abnormal stiffness and facilitating the design of the lift height h to maintain the stability of the F1 / h ratio.

[0170] When W1 / W2 is greater than 0.8, for example, W1 / W2 = 0.85, W1 is relatively large compared to W2. The width difference between the deformation section 22 and the tail of the valve plate 23 is small, resulting in an overly smooth width transition. This leads to excessively high overall stiffness K of the exhaust valve plate 20, which increases the valve plate opening resistance, causes dynamic response lag, and fails to adequately adapt to the compressor's exhaust pressure pulsations, thus reducing compressor efficiency. Furthermore, excessive stiffness increases the impact force during valve plate opening and closing, exacerbating valve seat wear and noise deterioration, affecting the compressor's operational comfort.

[0171] When W1 / W2 equals 0.8, compared to the case where W1 / W2 is greater than 0.8, the width transition from the valve plate tail 23 to the deformation section 22 is smoother, and the stress distribution at the connection is more uniform, which helps to avoid fatigue failure. At the same time, the width of the deformation section 22 is close to the width of the valve plate tail 23, which can ensure the structural strength of the deformation section 22. The overall stiffness K of the valve plate is near the upper limit of the reasonable range, which can be adapted to the operating conditions of compressors with high stiffness requirements.

[0172] When W1 / W2 is between 0.2 and 0.8, for example, W1 / W2 = 0.5, the transition from the tail 23 of the valve plate to the deformation section 22 is smoother, ensuring uniform stress distribution at the connection and effectively alleviating stress concentration, thus ensuring the reliability of the valve plate under long-term cyclic loading. On the other hand, the smooth connection between the tail 23 of the valve plate and the deformation section 22 ensures that the deformation section 22 has sufficient flexibility, allowing for flexible adjustment of elastic deformation, which helps to keep the lift height h within the range of 1.5 to 2.3 mm, avoiding abnormal stiffness. On the other hand, the tail 23 of the valve plate has sufficient width and the fixed end structure has reliable strength, which can achieve stable installation. At the same time, the width of the deformation section 22 is reasonable, taking into account both elastic deformation capacity and structural strength. It will not have problems such as insufficient strength due to the deformation section 22 being too narrow or excessive stiffness due to the deformation section 22 being too wide. In addition, the transition from the tail 23 of the valve plate to the deformation section 22 is smoother, which helps to distribute stress evenly and can reduce fatigue damage at the bending point of the deformation section 22 relative to the tail 23 of the valve plate, thus extending the service life of the valve plate.

[0173] Therefore, by limiting the ratio of W1 / W2 to a range of 0.2 to 0.8, this embodiment can effectively achieve a smooth width transition from the tail 23 of the valve plate to the deformation section 22, optimize the stress distribution at the bend of the tail 23 of the valve plate, avoid fatigue failure caused by stress concentration, and at the same time ensure the flexibility of the deformation section 22 to provide a suitable stiffness K, avoiding energy efficiency reduction and noise deterioration caused by excessive stiffness. In conjunction with the aforementioned parameter design, the overall design of the exhaust valve plate 20 is further improved, enhancing its operational reliability, dynamic response characteristics and adaptability under long-term cyclic loads, providing strong support for the efficient and low-noise operation of the compressor.

[0174] Please see Figure 5 In some embodiments, the thickness t of the exhaust valve plate 20 satisfies the following condition: 0.25mm≤t≤0.45mm.

[0175] For example, the thickness t of the exhaust valve plate 20 can be 0.25mm, 0.35mm, 0.45mm, etc.

[0176] The thickness t of the exhaust valve plate 20 can affect the material usage, structural rigidity, and mass distribution of the valve plate. It can be understood that the larger the thickness t of the exhaust valve plate 20, the stronger its structural rigidity and the higher its stiffness, but the mass of the exhaust valve plate 20 will also increase accordingly; conversely, the smaller the thickness t of the exhaust valve plate 20, the weaker its rigidity and the lower its stiffness, and the smaller its mass.

[0177] When t is less than 0.25mm, for example, t=0.22mm: the thickness of the exhaust valve plate 20 is relatively thin, which easily leads to low stiffness of the exhaust valve plate 20, making it lighter in weight. This weakens the exhaust valve plate 20's ability to resist exhaust pressure impacts. Under high pressure differential operating conditions of the compressor, the valve plate is prone to excessive deflection or even chattering, resulting in a sharp increase in stress at the valve plate root and a significant increase in the stress concentration factor. This may cause premature fatigue fracture of the valve plate, affecting its service life. Simultaneously, the low stiffness of the exhaust valve plate 20 makes it overly sensitive to exhaust pressure fluctuations, unable to maintain a stable opening and closing state, prone to opening and closing delays or jamming, affecting the compressor's exhaust efficiency, and even causing gas backflow.

[0178] When t equals 0.25mm, compared to when t is less than 0.25mm, the exhaust valve plate 20 can balance a certain level of impact resistance and opening / closing flexibility. The valve plate's ability to resist exhaust pressure impact basically meets the requirements of conventional compressor operating conditions. Under normal pressure differential, there will be no obvious excessive deflection or chattering. The stress at the root of the valve plate is within a controllable range, which can effectively avoid early fatigue fracture.

[0179] When t is greater than 0.45mm, for example, t=0.48mm, the thickness of the exhaust valve plate 20 is too thick. This can lead to excessive stiffness of the exhaust valve plate 20, increasing the opening resistance and requiring higher exhaust pressure to open the valve plate. This can easily result in increased compressor over-compression losses, decreased exhaust efficiency, and ultimately reduced energy efficiency. Simultaneously, an excessively thick exhaust valve plate 20 significantly increases the impact force on the limit plate and valve seat during opening and closing. This not only significantly increases impact noise, affecting the compressor's operational comfort, but may also damage the limit plate, valve seat, and other exhaust components, increasing equipment maintenance costs. Furthermore, excessive stiffness reduces the valve plate's opening and closing flexibility, leading to a lag in dynamic response and an inability to adapt well to the demands of exhaust pressure pulsations. This may result in delayed closing, exacerbating gas backflow losses.

[0180] When t equals 0.45mm, compared to when t is greater than 0.45mm, the exhaust valve plate 20 has a certain structural rigidity and outstanding impact resistance. Under high differential pressure conditions, it can also effectively avoid excessive deflection and flutter, ensuring stable operation of the valve plate. At the same time, it helps to avoid abnormal F1 / h ratio, thereby helping to avoid problems such as increased opening resistance and increased over-compression loss caused by excessive stiffness.

[0181] When t is between 0.25mm and 0.45mm, for example, t=0.35mm, the thickness of the exhaust valve plate 20 achieves an optimal balance between stiffness K, effective mass m, impact resistance, and opening / closing flexibility. On one hand, this ensures a smooth response of the exhaust valve plate 20 to exhaust pressure fluctuations, allowing it to quickly open under pressure and close promptly to reduce backflow losses. On the other hand, the exhaust valve plate 20 possesses sufficient impact resistance, preventing excessive deflection, flutter, and a sharp increase in root stress under normal high pressure differential conditions, effectively avoiding early fatigue fracture and extending valve plate lifespan. Simultaneously, the moderate thickness of the exhaust valve plate 20 keeps the impact force on the limit plate and valve seat during opening and closing within a controllable range, preventing significant impact noise and damage to the exhaust components. This makes it suitable for the normal and high-frequency operating conditions of most compressors, balancing energy efficiency, reliability, and operational comfort.

[0182] Furthermore, the thickness t of the exhaust valve plate 20 can be limited to work synergistically with the aforementioned design parameters. A reasonable value of t ensures that the stiffness of the exhaust valve plate 20 is within a preset range, working in conjunction with parameters such as lift height h, elastic force F1, W1 / W2, and L1 / d1 to achieve a stable F1 / h ratio and optimize the dynamic response characteristics of the valve plate. Simultaneously, a suitable thickness balances the valve plate's impact resistance and opening / closing flexibility, avoiding problems such as fatigue fracture, increased noise, and reduced energy efficiency caused by abnormal thickness. It also aligns with the dimensional design of the deformation section 22, valve plate head 21, and valve plate tail 23, further optimizing the stress distribution of the valve plate, reducing stress concentration, and improving its fatigue life. In addition, the range of t values ​​can be combined with the elastic modulus E of the valve plate material, further improving the accuracy of the theoretical calculation of stiffness K, providing a reliable basis for parameter optimization during the design phase, shortening the design cycle, and reducing testing costs.

[0183] It should be noted that the specific value of the valve plate thickness t needs to be determined comprehensively based on the overall design dimensions of the valve plate, material properties, compressor discharge pressure and operating conditions, to ensure that t is within the range of 0.25mm to 0.45mm. At the same time, it should be combined with parameters such as the valve plate head diameter d1, the average width W1 of the deformation section 22, and the length L1 of the deformation section 22 to achieve synergistic optimization of various performance parameters.

[0184] In summary, by limiting the thickness t of the exhaust valve plate 20 to the range of 0.25~0.45mm, this embodiment of the application helps to control the stiffness of the exhaust valve plate 20, balance the impact resistance, opening and closing flexibility and mass of the valve plate 20, and help avoid problems such as low stiffness, chattering and fatigue fracture caused by excessive thickness, while avoiding problems such as excessive stiffness, reduced energy efficiency, increased noise and damage to exhaust components caused by excessive thickness. With the aforementioned parameter design, the overall design of the exhaust valve plate 20 is further improved, enhancing its operational reliability, dynamic response characteristics, energy efficiency and service life, providing strong support for the efficient, low-noise and stable operation of the compressor.

[0185] The following examples illustrate specific embodiments. All of these embodiments can be used in household air conditioner rotary compressors with a cooling capacity of 2500W-3700W, and related tests were conducted using the same compressor. The comparative example uses the same material parameters as the exhaust valve plate 20 in the embodiments, but by designing different structural parameters, the F1 / h value of the exhaust valve plate 20 in the comparative example differs from that in the embodiments.

[0186] Example 1

[0187] Example 1 provides an exhaust valve plate 20 with a circular head, the exhaust valve plate 20 having an elastic modulus E = 210 GPa and a density ρ = 7.7 g / cm³. 3 .

[0188] The geometric parameters of the exhaust valve plate 20 are as follows: thickness t=0.381mm, lift height h=1.8mm, deformation section 22 length L1=12.0mm, exhaust valve plate 20 total length L2=36.1mm, valve plate head 21 diameter d1=9.8mm, deformation section 22 average width W1=3.2mm, and valve plate tail 23 average width W2=8.6mm.

[0189] The proportional relationships of the geometric parameters are calculated as follows: L1 / L2 = 0.332, L1 / d1 = 1.224, W1 / W2 = 0.372. Based on the theoretical expression for the elastic force F1 above, the elastic force of the exhaust valve plate 20 is 2.81 N. The measured elastic force of the exhaust valve plate 20 at a lift height h of 1.8 mm is also 2.81 N. Therefore, F1 / h = 1.56.

[0190] Example 2

[0191] Example 2 provides an exhaust valve plate 20 with a circular head, the exhaust valve plate 20 having an elastic modulus E = 210 GPa and a density ρ = 7.7 g / cm³. 3 .

[0192] The geometric parameters of the exhaust valve plate 20 are as follows: thickness t=0.381mm, lift height h=1.8mm, deformation section 22 length L1=12.4mm, exhaust valve plate 20 total length L2=36.1mm, valve plate head 21 diameter d1=9.8mm, deformation section 22 average width W1=4.0mm, and valve plate tail 23 average width W2=8.6mm.

[0193] The proportional relationships of the geometric parameters are calculated as follows: L1 / L2 = 0.343, L1 / d1 = 1.265, W1 / W2 = 0.465. Based on the theoretical expression for the elastic force F1 mentioned earlier, the elastic force is 3.62 N, from which we can obtain F1 / h = 2.03.

[0194] Example 3

[0195] Example 3 provides a fan-shaped exhaust valve plate 20 as supplementary verification for different head shapes. The exhaust valve plate 20 has an elastic modulus E = 210 GPa and a density ρ = 7.7 g / cm³. 3 .

[0196] The geometric parameters of the exhaust valve plate 20 are as follows: thickness t=0.305mm, lift height h=1.7mm, deformation section 22 length L1=12.0mm, exhaust valve plate 20 total length L2=38.9mm, valve plate head 21 diameter d1=10.8mm, deformation section 22 average width W1=5.0mm, valve plate tail 23 average width W2=8.6mm;

[0197] The proportional relationships of the geometric parameters are calculated as follows: L1 / L2 = 0.308, L1 / d1 = 1.111, W1 / W2 = 0.581. Based on the theoretical expression for the elastic force F1 from the previous text, the elastic force is 2.7N. The measured elastic force of the exhaust valve plate 20 at a lift height h of 1.8mm is also 2.7N, thus F1 / h = 1.57.

[0198] Comparative Example

[0199] The exhaust valve plate 20 of the comparative example has the same material parameters as the exhaust valve plate 20 in Examples 1, 2 and 3. By designing different structural parameters, it exhibits different F1 / h values. The F1 / h value of the exhaust valve plate 20 of the comparative example is 1.27.

[0200] The above Examples 1, 2, 3 and the comparative example were tested under the same working conditions, and the test results are as follows:

[0201] At a rated operating frequency of 120Hz, Example 1 showed a 2.2% improvement in energy efficiency ratio and a 1-2dB improvement in noise in the 3150-5000Hz frequency band compared to the comparative example; Example 2 showed a 2.3% improvement in energy efficiency ratio and a 2.5-4.2dB improvement in noise in the same frequency band compared to the comparative example; Example 3 showed a 1.5% improvement in energy efficiency ratio and a 1-2.3dB improvement in noise in the same frequency band compared to the comparative example. Here, energy efficiency ratio is the ratio of the compressor's cooling capacity to its power. The above test results indicate that by controlling the F1 / h ratio within a preset range, the dynamic response characteristics of the exhaust valve plate 20 can be effectively optimized, reducing high-pressure gas backflow losses and valve plate opening and closing impact noise, thereby improving the compressor's energy efficiency and operational comfort.

[0202] In summary, the embodiments of this application, through reasonable design of geometric parameters, control of various proportional relationships and F1 / h ratio, can effectively improve the compressor's energy efficiency ratio and reduce operating noise, and have good design tolerance and universality, which can meet the usage requirements of household air conditioner rotary compressors.

[0203] The embodiments or implementation methods in this application are described in a progressive manner. Each embodiment focuses on the differences from other embodiments, and the same or similar parts between the embodiments can be referred to each other.

[0204] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0205] In the description of this application, it should be understood that the terms “comprising” and “having” as used herein, and any variations thereof, are intended to cover non-exclusive inclusion, for example, a process, method, display structure, product, or device that includes a series of steps or units is not necessarily limited to those steps or units that are expressly listed, but may include other steps or units that are not expressly listed or that are inherent to such process, method, product, or device.

[0206] Although terms such as “first,” “second,” and “third” may be used in this application to describe various components, parts, regions, layers, or sections, these components, parts, regions, layers, or sections are not limited to these terms. Rather, these terms are used only to distinguish one component, part, region, layer, or section from another. Therefore, without departing from the teachings of the examples described in this application, the first component, part, region, layer, or section mentioned in the examples may also be referred to as the second component, part, region, layer, or section. 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 indicated technical features. Thus, a feature defined as “first” or “second” may explicitly or implicitly include at least one of that feature. In the description of this application, “multiple” means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0207] The term “exemplary” is used in this application to mean serving as an example, instance, or illustration. Any aspect or design described as “exemplary” in this application is not necessarily to be construed as advantageous compared to other aspects or designs. Rather, the use of the term “exemplary” is intended to present the concept in a concrete manner. As used in this application, the term “or” is intended to mean an inclusive “or” rather than an exclusive “or.” That is, unless otherwise specified or clear from the context, “X applies A or B” is intended to mean any of the natural inclusive arrangements. That is, “X applies A or B” satisfies any of the foregoing examples if X applies A; X applies B; or both X applies A and B. Additionally, unless otherwise specified or clear from the context to refer to the singular form, the articles “a” and “an” as used in this application and the appended claims are generally understood to mean “one or more.”

[0208] Unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated.

[0209] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. An exhaust valve plate, characterized in that, The exhaust valve plate (20) includes a valve plate head (21) and a valve plate tail (23). The valve plate tail (23) is configured to be connected to the cylinder head (10) of the cylinder. The valve plate head (21) is configured to be opposite to the exhaust valve hole (11) on the cylinder head (10) and can move relative to the cylinder head (10) to open or close the exhaust valve hole (11). When the valve plate head (21) closes the exhaust valve hole (11), the point opposite to the center of the valve plate head (21) and the exhaust valve hole (11) is recorded as reference point Q. During the process of the valve head (21) moving relative to the cylinder head (10) to open the exhaust valve hole (11), when the reference point Q is raised to the lift height h, the elastic force F1 on the valve head (21) and the lift height h satisfy the following relationship: 1.5≤F1 / h≤2.2; 1.5≤h≤2.3; The unit of the elastic force F1 is N, and the unit of the lift height h is mm.

2. The exhaust valve plate according to claim 1, characterized in that, The exhaust valve plate (20) further includes a deformation section (22), which is located between the valve plate head (21) and the valve plate tail (23) to connect the valve plate head (21) and the valve plate tail (23). With the center of the exhaust valve hole (11) as the central axis, the average diameter of each differential circular arc segment in the valve head (21) is taken as the diameter of the valve head (21), d1; the average width of the deformation segment (22) is W1; the length of the deformation segment (22) is L1; the arrangement direction of the valve head (21), the deformation segment (22), and the valve tail (23) is the length direction of the exhaust valve (20); the total length of the exhaust valve (20) is L2; ​​the thickness of the exhaust valve (20) is t; the units of d1, W1, L1, L2, and t are all mm, and the following condition is satisfied: Wherein, E is the material elastic modulus of the exhaust valve plate (20), in GPa; k is the first correction coefficient, S is the shape coefficient, and k and S are determined according to the structure of the valve plate head (21); the structure of the valve plate head (21) includes a fan-shaped structure, a circular structure, or a first shape structure, and the first shape structure includes other shape structures besides the fan-shaped structure and the circular structure; The fan-shaped structure, the circular structure, and the first shape structure each correspond to different k, and the fan-shaped structure, the circular structure, and the first shape structure each correspond to different S.

3. The exhaust valve plate according to claim 2, characterized in that, When the structure of the valve head (21) is the fan-shaped structure, k=32 and S=1.

1.

4. The exhaust valve plate according to claim 3, characterized in that, The fan-shaped structure has two intersecting first sides (211), both of which are circular arcs with a radius of R1, and the included angle between the two first sides (211) is α. Among them, 60mm≤R1≤100mm, 15°≤α≤75°.

5. The exhaust valve plate (20) according to claim 2, characterized in that, When the structure of the valve head (21) is the circular structure, k=25 and S=0.

9.

6. The exhaust valve plate according to claim 5, characterized in that, The circular structure has two opposing second sides (212) on the side facing the deformed segment (22). Both second sides (212) are arc edges with a radius of R2, where R2 is in mm. R2 and d1 satisfy the following relationship: 0.05≤R2 / d1≤2.

5.

7. The exhaust valve plate according to claim 2, characterized in that, When the structure of the valve head (21) is the first shape structure, k=30 and S=1.

0.

8. The exhaust valve plate according to claim 2, characterized in that, The exhaust valve plate (20) is located in a compressor containing the cylinder, and the compressor operates at a frequency of 120 Hz and an exhaust pressure of 2.93 MPa, wherein d1, W1, L1, L2 and t satisfy the following condition: Wherein, ρ is the material density of the exhaust valve plate (20), in g / cm³, and e is the natural constant, taken as 2.

718.

9. The exhaust valve plate according to any one of claims 2-8, characterized in that, L1 and d1 satisfy the following relationship: 0.7≤L1 / d1≤1.

4.

10. The exhaust valve plate according to any one of claims 2-8, characterized in that, L1 and L2 satisfy the following relationship: 0.3≤L1 / L2≤0.

5.

11. The exhaust valve plate according to any one of claims 2-8, characterized in that, The average width of the tail (23) of the valve plate is W2, and W2 and the average width W1 of the deformed segment (22) satisfy the following condition: 0.2≤W1 / W2≤0.

8.

12. The exhaust valve plate according to any one of claims 1-8, characterized in that, The thickness t of the exhaust valve plate (20) satisfies the following condition: 0.25mm≤t≤0.45mm.

13. A cylinder assembly, characterized in that, include: The cylinder block; Cylinder head (10), the cylinder head (10) seat is provided on the top of the cylinder body, and the cylinder head (10) has an exhaust valve hole (11). As described in any one of claims 1-12, the exhaust valve plate (20) has a valve plate tail (23) connected to the cylinder head (10), and the exhaust valve plate head (21) is disposed opposite to the exhaust valve hole (11) and can move relative to the cylinder head (10) to open or close the exhaust valve hole (11).

14. A compressor, characterized in that, Includes an exhaust valve plate (20) as described in any one of claims 1-12, or includes a cylinder assembly as described in claim 13, the cylinder assembly being disposed within the cylinder body.

15. A refrigeration device, characterized in that, It includes the exhaust valve plate (20) as described in any one of claims 1-12, or the cylinder assembly as described in claim 13, or the compressor as described in claim 14.

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