Air suction valve group, compressor and refrigeration equipment

Abstract

The invention discloses an air suction valve group, a compressor and refrigeration equipment, and relates to the technical field of compressors. The air suction valve set comprises a valve plate and a valve body, the valve body is connected with the valve plate, two reeds of the valve plate are connected into the notch of the body through fixed sections, and the free sections of the reeds can cover the air suction holes in the valve body. Due to the fact that the number of the reeds is two, and the number of the air suction holes is two, the air suction amount is larger than that of a single-hole scheme. In order to improve the opening degree of the reed, the distance between the two first edge sections is gradually reduced or kept unchanged, the distance between the two second edge sections is gradually reduced or kept unchanged, the distance between the two third edge sections is gradually increased, and the distance between the two fourth edge sections is gradually increased; therefore, when the free section tilts under the action of pressure, the free section is eccentrically opened, the opening angle of the free section can be increased to a certain extent, and then the air inflow is improved.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to an intake valve assembly, a compressor, and refrigeration equipment. Background Technology

[0002] Refrigerator compressors can be reciprocating compressors. The compressor's suction efficiency and suction volume are usually related to the reed valve on the suction valve assembly. When the compressor draws in air, the reed valve opens the suction port; when it discharges air, the reed valve closes the suction port. If the suction port closes too slowly, some refrigerant will flow back, resulting in a reduction in the effective suction volume. When the compressor operates at high frequencies of 72Hz and above, the response speed of the reed valve is crucial. To improve the closing speed of the reed valve and reduce backflow, the stiffness of the reed valve is usually increased, for example, by using a wider valve to increase the spring speed. While this approach results in a faster closing speed, it also reduces the angle the reed valve can open, thus reducing the intake volume and making it difficult to effectively improve the compressor's energy efficiency. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes an intake valve assembly that can increase the intake volume while improving the reed response speed.

[0004] The present invention also proposes a compressor and refrigeration equipment having the above-mentioned suction valve assembly.

[0005] According to a first aspect of the present invention, an intake valve assembly includes: a valve body having two intake holes arranged along a first direction; A valve plate is connected to the valve body. The valve plate includes a body and two tongue springs. The body has a notch. The two tongue springs are respectively disposed in the notch and arranged along the first direction. The tongue springs include a fixed section, a swing arm section and a free section connected in sequence. The fixed section is fixedly connected to the inner wall of the notch. The free section is configured to swing relative to the body and cover the corresponding air intake hole. Wherein, each of the swing arm segments includes a first edge segment on the side facing the other swing arm segment, the first edge segment being connected to the edge of the free segment; each of the swing arm segments includes a second edge segment on the side facing away from the other swing arm segment; each of the fixed segments includes a third edge segment on the side facing the other fixed segment; and each of the fixed segments includes a fourth edge segment on the side facing away from the other fixed segment. Along a second direction perpendicular to the first direction, the distance between two first edge segments gradually decreases or remains constant, the distance between two second edge segments gradually decreases or remains constant, the distance between two third edge segments gradually increases, and the distance between two fourth edge segments gradually increases.

[0006] The intake valve assembly according to embodiments of the present invention has at least the following beneficial effects: By connecting the valve body and valve plate, the two tongue springs of the valve plate are connected to the notch in the body through a fixed section. The free section of the tongue spring can cover the intake port on the valve body. Therefore, when the compressor draws in air, the free section opens the intake port, and when it discharges air, the free section closes the intake port. Since there are two tongue springs and two intake ports, the intake volume is larger than that of a single-port design. Therefore, by increasing the overall strength of the tongue spring, the rebound speed of the tongue spring can be increased, and the response speed of closing the intake port can be faster, thereby reducing the backflow and improving the energy efficiency of the compressor. To increase the opening degree of the tongue spring, the distance between the two first edge sections is gradually reduced or remains constant, the distance between the two second edge sections is gradually reduced or remains constant, the distance between the two third edge sections is gradually increased, and the distance between the two fourth edge sections is gradually increased. Therefore, when the free section tilts up under pressure, the free section opens eccentrically, which can increase the opening angle of the free section to a certain extent, thereby increasing the intake volume.

[0007] According to some embodiments of the present invention, the distance between the first edge segment and the second edge segment gradually decreases along a direction away from the free segment; or, Along a direction away from the free segment, the first edge segment gradually approaches the second edge segment.

[0008] According to some embodiments of the present invention, the distance between the third edge segment and the fourth edge segment gradually increases along a direction away from the swing arm segment; or, Along a direction away from the swing arm segment, the third edge segment gradually moves away from the fourth edge segment.

[0009] According to some embodiments of the present invention, on a projection plane perpendicular to the thickness direction of the valve plate, the edge of the free segment includes an arc edge segment, the center point of the arc edge segment is point O, and a straight line passing through point O and perpendicular to the first direction is defined as a first reference line L1. The end of the first edge segment facing the free segment and the end of the second edge segment facing the free segment are respectively located on the side of the first reference line L1 away from the other tongue.

[0010] According to some embodiments of the present invention, on a projection plane perpendicular to the thickness direction of the valve plate, the edge of the free segment includes an arc edge segment, the center point of the arc edge segment is point O, the center point of the line connecting the two sides at the maximum width of the fixed segment is point A, the line connecting point O and point A is defined as the second reference line L2, and the projected outer contour line of the tongue intersects with the second reference line L2.

[0011] According to some embodiments of the present invention, the first edge segment, the second edge segment, the third edge segment and the fourth edge segment are each constructed as straight edges, the included angle between the second edge segment and the fourth edge segment is θ, and the included angle between the first edge segment and the third edge segment is β, satisfying: θ≤β.

[0012] According to some embodiments of the present invention, the bending ratio of the tongue spring is defined as S, S=θ / β, satisfying: 0.7≤S≤0.86.

[0013] According to some embodiments of the present invention, the included angle θ between the second edge segment and the fourth edge segment satisfies: 95° ≤ θ ≤ 140°; and / or, The included angle β between the first edge segment and the third edge segment satisfies: 135°≤β≤170°.

[0014] According to some embodiments of the present invention, the second edge segment and the fourth edge segment are connected by a first arc-shaped segment; and / or, The first edge segment and the third edge segment are connected by a second arc segment.

[0015] According to some embodiments of the present invention, the edge of the free segment includes an arc edge segment, and the second edge segment is tangent to the arc edge segment.

[0016] According to some embodiments of the present invention, the two tongue reeds are arranged symmetrically along an axis of symmetry, which is perpendicular to the first direction.

[0017] The compressor according to a second aspect of the present invention includes the suction valve assembly described in the above embodiments.

[0018] The compressor according to embodiments of the present invention has at least the following beneficial effects: By employing the intake valve assembly of the first aspect embodiment, the intake valve assembly is connected by a valve body and a valve plate. Two tongue springs on the valve plate are connected to the notch in the body via a fixed section. The free section of the tongue springs can cover the intake port on the valve body. Therefore, when the compressor draws in air, the free section opens the intake port, and when it discharges air, the free section closes the intake port. Since there are two tongue springs and two intake ports, the intake volume is larger than that of a single-port design. Therefore, by increasing the overall strength of the tongue springs, the rebound speed of the tongue springs can be increased, resulting in a faster response speed to close the intake port, thereby reducing backflow and improving the compressor's energy efficiency. To increase the opening degree of the tongue springs, the distance between the two first edge sections is gradually reduced or remains constant, the distance between the two second edge sections is gradually reduced or remains constant, the distance between the two third edge sections is gradually increased, and the distance between the two fourth edge sections is gradually increased. Therefore, when the free section tilts up under pressure, the free section opens eccentrically, which can increase the opening angle of the free section to a certain extent, thereby increasing the intake volume.

[0019] A refrigeration device according to a third aspect of the present invention includes the compressor described in the above embodiments.

[0020] The refrigeration device according to embodiments of the present invention has at least the following beneficial effects: In the compressor of the second embodiment, the compressor's intake valve assembly is connected by a valve body and a valve plate. Two springs on the valve plate are connected to a notch in the body via a fixed section. The free section of the springs can cover the intake port on the valve body. Therefore, when the compressor draws in air, the free section opens the intake port, and when it discharges air, the free section closes the intake port. Since there are two springs and two intake ports, the intake volume is larger than that of a single-port design. Therefore, by increasing the overall strength of the springs, the springs' rebound speed can be improved, resulting in a faster response to close the intake port, thereby reducing backflow and improving the compressor's energy efficiency. To increase the opening degree of the springs, the distance between the two first edge sections is gradually reduced or remains constant, the distance between the two second edge sections is gradually reduced or remains constant, the distance between the two third edge sections is gradually increased, and the distance between the two fourth edge sections is gradually increased. Therefore, when the free section tilts up under pressure, it opens eccentrically, which can increase the opening angle of the free section to a certain extent, thereby increasing the intake volume.

[0021] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0022] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein: Figure 1 This is an exploded schematic diagram of an intake valve assembly according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the valve plate according to an embodiment of the present invention; Figure 3 This is a schematic diagram of a tongue reed structure according to an embodiment of the present invention; Figure 4 This is a bar chart comparing the high-frequency capabilities of an intake valve assembly and a single valve structure according to an embodiment of the present invention. Figure 5 This is a bar chart comparing the low-frequency capabilities of an intake valve assembly and a single valve structure according to an embodiment of the present invention.

[0023] Figure label: Intake valve assembly 1000; Valve body 100; intake port 110; first exhaust port 120; first mounting hole 130; Valve plate 200; body 210; second vent 211; second mounting hole 212; notch 214; tongue spring 220; fixed section 221; fourth edge section 2211; third edge section 2212; swing arm section 222; second edge section 2221; first edge section 2222; free section 223; arc edge section 2231; transition edge section 2232; first arc section 224; second arc section 225; filler plate 230. Detailed Implementation

[0024] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0025] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0026] In the description of this invention, "several" means one or more, "more than" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0027] In the description of this invention, unless otherwise explicitly defined, terms such as "set up," "install," and "connect" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this invention in conjunction with the specific content of the technical solution.

[0028] During the operation of a reciprocating compressor, the piston reciprocates within the cylinder. When the piston moves away from the valve body, a negative pressure is created inside the cylinder. At this time, refrigerant gas enters the cylinder through the suction port, and the reed valve opens under the pressure difference, allowing the refrigerant to enter the cylinder through the suction port. When the piston moves in the reverse direction to compress, the pressure inside the cylinder increases, and the reed valve needs to quickly close the suction port to prevent the refrigerant that has already entered the cylinder from flowing back.

[0029] When the compressor operates at a high frequency of 72Hz or higher, the compressor motor speed is 4320 r / min or higher. The piston reciprocating cycle is short, and the reed needs to complete the opening and closing action in a very short time. If the reed closes too slowly, the suction port will still be open at the beginning of the compression stroke, and some refrigerant will flow back from the cylinder to the suction side, resulting in a reduction in effective suction volume and a decrease in compressor efficiency.

[0030] Existing technologies typically employ a structure where a single reed covers a single intake port. To improve the reed's response speed under high-frequency conditions, the overall stiffness of the reed needs to be increased, for example, by increasing its width or thickness, giving it greater rebound force and thus accelerating the closing speed. However, with increased stiffness, the angle at which the reed is drawn open during the intake stroke decreases, reducing the effective cross-sectional area of ​​the intake channel and resulting in insufficient air intake, making it difficult to maintain a sufficient intake volume while reducing backflow.

[0031] To solve the above problems, refer to Figure 1 , Figure 2 and Figure 3 As shown, an intake valve assembly 1000 according to an embodiment of the present invention can be used in a compressor, such as a reciprocating compressor. The intake valve assembly 1000 of this embodiment includes a valve body 100 and a valve plate 200. The valve body 100 has two intake holes 110 arranged along a first direction. The valve plate 200 is connected to the valve body 100 and includes a body 210 and two springs 220. The body 210 has a notch 214, and the two springs 220 are respectively disposed in the notch 214 and arranged along the first direction. The spring 220 includes a fixed section 221, a swing arm section 222, and a free section 223. One end of the fixed section 221 is fixedly connected to the inner wall of the notch 214, one end of the swing arm section 222 is connected to the other end of the fixed section 221, and the other end of the swing arm section 222 is connected to the free section 223. The free section 223 is configured to swing relative to the body 210 and to cover the corresponding intake hole 110.

[0032] The edge of each swing arm segment 222 facing the other swing arm segment 222 includes a first edge segment 2222, which is connected to the edge of the free segment 223. The edge of each swing arm segment 222 facing away from the other swing arm segment 222 includes a second edge segment 2221; the edge of each fixed segment 221 facing the other fixed segment 221 includes a third edge segment 2212; and the edge of each fixed segment 221 facing away from the other fixed segment 221 includes a fourth edge segment 2211.

[0033] Reference Figure 2 and Figure 3As shown, along the second direction perpendicular to the first direction, the distance between the two first edge segments 2222 gradually decreases or remains constant, the distance between the two second edge segments 2221 gradually decreases or remains constant, the distance between the two third edge segments 2212 gradually increases, and the distance between the two fourth edge segments 2211 gradually increases.

[0034] It should be noted that the second direction is a single direction, as shown in the example below. Figure 2 As shown in the figure, the distances between the two first edge segments 2222, the two second edge segments 2221, the two third edge segments 2212, and the two fourth edge segments 2211 all refer to the distances along the first direction.

[0035] In this embodiment, two suction holes 110 are arranged along the first direction on the valve body 100, and two corresponding tongue springs 220 are provided on the valve plate 200. Compared with a single suction hole 110 and a single tongue spring 220, the total flow area of ​​the two suction holes 110 is larger. During the same suction stroke time, the refrigerant can enter the cylinder through both suction holes 110 simultaneously, increasing the suction volume. Based on this premise, sufficient suction volume can still be guaranteed while increasing the overall strength of the tongue spring 220. Therefore, after increasing the stiffness of the tongue spring 220, the rebound speed of the tongue spring 220 is faster, and it can close the suction hole 110 more quickly at the beginning of the compression stroke, reducing the refrigerant backflow and thus improving the energy efficiency of the compressor under high-frequency operating conditions.

[0036] Each spring 220 consists of three parts: a fixed section 221, a swing arm section 222, and a free section 223. One end of the fixed section 221 is fixedly connected to the inner wall of the notch 214, serving as a root constraint for the spring 220. The swing arm section 222 extends from the other end of the fixed section 221, connecting the fixed section 221 and the free section 223. The length and curvature of the swing arm section 222 determine the flexibility and resilience of the spring 220. The free section 223 is located at the end of the spring 220 and swings relative to the body 210 under pressure differential, thereby opening or closing the corresponding intake port 110.

[0037] In this embodiment, the distance between the two first edge segments 2222 gradually decreases or remains constant, the distance between the two second edge segments 2221 gradually decreases or remains constant, the distance between the two third edge segments 2212 gradually increases, and the distance between the two fourth edge segments 2211 gradually increases. Therefore, the overall orientation of the swing arm segment 222 is towards the central region between the two tongue springs 220, while the overall orientation of the fixed segment 221 is towards the outside, away from the central region. The swing arm segment 222 and the fixed segment 221 form a bend at the connection point, roughly constituting two parts with a certain angle. From the perspective of a single tongue spring 220, the extension direction of the fixed segment 221 and the extension direction of the swing arm segment 222 are not on the same straight line; the tongue spring 220 is bent. This bent shape gives the tongue spring 220 an asymmetrical geometric configuration, meaning that the curve shapes of the inner and outer edges of the tongue spring 220 are inconsistent, and the difference in cross-sectional stiffness distribution between the inner and outer edges is significant.

[0038] When the refrigerant gas pushes the free section 223 to open the intake port 110, due to the asymmetry of the geometry of the spring 220, the effective arm length on the inner side of the spring 220 is different from that on the outer side, resulting in a difference in bending stiffness between the inner and outer sides during bending deformation. Under the same differential pressure load, the deformation on the side with lower stiffness is greater, and the edge of the free section 223 rises more significantly on the side with lower stiffness. Compared with the symmetrical configuration of the spring 220, at the same stiffness level, the eccentric opening method increases the maximum deflection angle of the free section 223, increases the gap between the edge of the free section 223 and the surface of the valve body 100, increases the flow cross-sectional area of ​​the refrigerant flowing through the intake port 110, and increases the amount of refrigerant entering the cylinder per unit time.

[0039] In summary, through a combination of edge direction design—with the distance between the two first edge segments 2222 gradually decreasing or remaining constant, the distance between the two second edge segments 2221 gradually decreasing or remaining constant, the distance between the two third edge segments 2212 gradually increasing, and the distance between the two fourth edge segments 2211 gradually increasing—the swing arm segment 222 and the fixed segment 221 form a bent configuration with a certain included angle, increasing the asymmetry of the spring 220 itself. During the intake phase, the free segment 223 increases its opening by opening eccentrically, increasing the refrigerant intake volume. During the exhaust phase, due to the smaller mass and higher natural frequency of the free segment 223 of each spring 220, the free segment 223 quickly closes the intake port 110 under the action of elastic restoring force and cylinder pressure, reducing the refrigerant return flow. The two springs 220 work together to increase the intake opening while maintaining a high closing response speed, thereby improving intake efficiency and compressor energy efficiency under high-frequency compressor operation conditions.

[0040] Effect reference Figure 4 As shown, Figure 4 The bar chart reflects the improvement in compressor performance during high-frequency operation by the intake valve assembly 1000 in this embodiment. The left side shows the traditional single-valve structure, which has only one reed 220; the right side shows the solution of this embodiment. High-frequency capability refers to the effective intake volume. Taking the high-frequency capability of the single-valve structure as 100 as a benchmark, the high-frequency capability of this embodiment is 108, representing an improvement of approximately 8%.

[0041] When the compressor operates at low frequency, with a speed of 1620 r / min or below, the piston reciprocating cycle is relatively long, giving the reed 220 sufficient time to complete its closing action. Therefore, the impact of the return flow on the effective intake volume is relatively small. Under low-frequency conditions, compressor efficiency is of greater concern, and efficiency is negatively correlated with the opening resistance of the reed 220. The lower the opening resistance, the faster the reed 220 is pushed open during the initial intake phase, resulting in a longer effective intake time and less work required to push the reed 220 open.

[0042] Reference Figure 5 As shown, Figure 5 The bar chart reflects the improvement in compressor performance at low frequencies by the intake valve assembly 1000 in this embodiment. The left side shows the traditional single-valve structure, which has only one reed 220; the right side shows the structure of this embodiment. Low-frequency capability refers to the effective intake volume / compression work. Using the low-frequency capability of the single-valve structure as a baseline of 1, the low-frequency capability of this embodiment is 1.03, representing an improvement of approximately 3%.

[0043] Reference Figure 1 and Figure 2 As shown in the embodiment of the present invention, on the projection plane perpendicular to the thickness direction of the valve plate 200, the edge of the free segment 223 includes an arc edge segment 2231, the center point of the arc edge segment 2231 is point O, and the straight line passing through point O and perpendicular to the first direction is defined as the first reference line L1. The end of the first edge segment 2222 facing the free segment 223 and the end of the second edge segment 2221 facing the free segment 223 are respectively located on the side of the first reference line L1 away from the other tongue spring 220. Therefore, it can be regarded that the swing arm segment 222 is connected to the side of the free segment 223 away from the other free segment 223, that is, the swing arm segment 222 is connected to the outside of the free segment 223.

[0044] When a negative pressure forms inside the cylinder during the intake stroke, the refrigerant gas pushes the free section 223 upwards. Because the swing arm section 222 is connected to the outside of the free section 223, the constraint force on the inside of the free section 223 is smaller, while the constraint force on the outside is larger. Under the action of gas pressure, the free section 223 tends to open eccentrically, and the upward amplitude of the inside of the free section 223 is greater. This eccentric opening method allows the free section 223 to achieve a larger opening angle while maintaining high overall rigidity. Compared with the scheme where the swing arm section 222 is connected to the center of the free section 223, the maximum opening of the free section 223 is increased, and the effective flow cross-sectional area of ​​the intake port 110 is increased, thereby increasing the intake volume of each intake stroke while maintaining the rapid closing capability of the tongue spring 220.

[0045] In summary, this embodiment increases the total suction area by setting up a dual-channel suction structure with two tongue springs 220 and two suction ports 110; at the same time, by connecting the swing arm section 222 to the eccentric position of the free section 223, the free section 223 can be opened eccentrically to increase the opening degree. These two measures combined ensure that the tongue springs 220, while maintaining high stiffness and a fast closing response speed, still provide sufficient intake volume, reduce refrigerant backflow, and improve the energy efficiency of the reciprocating compressor under high-frequency operating conditions.

[0046] It should be noted that the division of the free section 223, the swing arm section 222, and the fixed section 221 is as follows: Figure 3 As shown by dashed lines L3 and L4, dashed line L3 connects the first edge segment 2222 and the second edge segment 2221 towards the free segment 223, serving as the boundary line between the free segment 223 and the swing arm segment 222. The second edge segment 2221 and the fourth edge segment 2211 are connected by a first arc segment 224, and the first edge segment 2222 and the third edge segment 2212 are connected by a second arc segment 225. Dashed line L4 connects the first edge segment 2222 and the first arc segment 224 towards the fixed segment 221, serving as the boundary line between the swing arm segment 222 and the fixed segment 221.

[0047] Reference Figure 2 As shown, in an embodiment of the present invention, the distance between the first edge segment 2222 and the second edge segment 2221 gradually decreases along the direction away from the free segment 223; or, in other words, the first edge segment 2222 gradually approaches the second edge segment 2221 along the direction away from the free segment 223. Therefore, along the direction away from the free segment 223, one swing arm segment 222 gradually approaches the other swing arm segment 222.

[0048] Understandably, as the swing arm segment 222 extends from the free segment 223 towards the fixed segment 221, it gradually moves closer to the side where the other swing arm segment 222 is located. The swing arm segment 222 tilts inward in the second direction, creating an angle between the extension direction of the swing arm segment 222 and the opening direction of the free segment 223. When the free segment 223 tilts up under the influence of gas pressure difference, the constraint force exerted by the swing arm segment 222 on the free segment 223 deviates from the geometric center of the free segment 223, with the constraint force on the outer side of the free segment 223 being greater than that on the inner side. This uneven distribution of torque makes the free segment 223 produce a more pronounced eccentric effect during the opening process, further increasing the inward tilting amplitude. The structural asymmetry of the tongue spring 220 itself is improved, making the eccentric opening effect of the free segment 223 more obvious, increasing the opening angle, and thus increasing the intake volume in each inhalation stroke.

[0049] Reference Figure 2 As shown, in an embodiment of the present invention, along the second direction, one fixed segment 221 is gradually positioned away from the other fixed segment 221. The fixed segment 221 serves as the root of the tongue spring 220, with one end fixedly connected to the inner wall of the notch 214, and is the starting position where the tongue spring 220 bears bending loads and rebound forces. In the second direction, as the fixed segment 221 extends from its connection point with the inner wall of the notch 214 towards the swing arm segment 222, it gradually shifts away from the other fixed segment 221, meaning that the extension directions of the two fixed segments 221 each extend outwards.

[0050] In conjunction with the characteristic of the swing arm segment 222 gradually moving inward in the above embodiment, the fixed segment 221 moves away from the outside while the swing arm segment 222 moves inward, with their extension directions showing opposite trends. This design creates a distinct bending transition between the fixed segment 221 and the swing arm segment 222, and the overall contour of the tongue spring 220 from the fixed segment 221 to the swing arm segment 222 and then to the free segment 223 exhibits a curved direction, further increasing the asymmetry of the tongue spring 220.

[0051] From the perspective of eccentricity, the outward extension of the fixed section 221 shifts the constraint position at the root of the tongue spring 220 outward, while the inward extension of the swing arm section 222 connects to the outer side of the free section 223. This results in a greater difference in the stiffness distribution of the entire tongue spring 220 along the width of the free section 223. The outer side of the free section 223 forms a longer lever arm path through the swing arm section 222 and the fixed section 221, while the inner side has relatively less constraint. When the free section 223 is lifted by gas pressure, the inner deformation is greater, further increasing the eccentric opening. This increases the maximum opening of the free section 223, increases the effective flow area of ​​the intake port 110, and increases the amount of refrigerant entering the cylinder through the intake port 110 during each intake stroke.

[0052] Meanwhile, the outward expansion of the fixed section 221 can increase the contact area and connection width between the fixed section 221 and the inner wall of the notch 214, making the connection at the root of the fixed section 221 more stable. During the long-term high-frequency reciprocating motion of the tongue spring 220, the risk of fatigue damage caused by stress concentration at the root of the fixed section 221 is reduced, which is conducive to improving the service life and working stability of the tongue spring 220.

[0053] Reference Figure 2 and Figure 3 As shown, in an embodiment of the present invention, the distance between the third edge segment 2212 and the fourth edge segment 2211 gradually increases along the direction away from the swing arm segment 222. Alternatively, another interpretation could be that the third edge segment 2212 gradually moves away from the fourth edge segment 2211 along the direction away from the swing arm segment 222. Therefore, the fixed segment 221 exhibits a shape that is wider closer to the root and narrower closer to the swing arm segment 222, that is, the width of the fixed segment 221 gradually increases from the direction of the swing arm segment 222 towards the root.

[0054] Using the above scheme, the cross-sectional width at the connection between the fixed section 221 and the inner wall of the notch 214 is relatively large. The fixed section 221, as the root bearing area of ​​the spring 220, bears repeated bending stress during the opening and closing of the free section 223. The larger the width of the fixed section 221 at the connection, the larger its moment of inertia and the higher its overall bending stiffness. The increase in stiffness directly affects the rebound performance of the spring 220: when the compression stroke begins and the cylinder pressure increases, the free section 223 needs to quickly return to its initial position under the rebound force of the spring 220, closing the intake port 110. The higher the stiffness of the fixed section 221, the stronger the ability of the spring 220 to store elastic potential energy, the faster the rebound speed of the free section 223, and the shorter the time required to close the intake port 110.

[0055] Under high-frequency operation of the compressor, each intake and exhaust cycle is very short, and the reed 220 needs to close within a very short time. If the fixed section 221 is too narrow or lacks sufficient rigidity, the reed 220 will rebound slowly, and the free section 223 will remain open at the beginning of the compression stroke. Some of the refrigerant already in the cylinder will flow back from the intake port 110 to the intake side, resulting in a loss of effective intake volume. By moving the inner and outer edges of the fixed section 221 further apart, increasing its width and cross-sectional rigidity, the rebound speed of the free section 223 is improved, the response time to close the intake port 110 is shortened, the refrigerant backflow is reduced, and the effective intake volume of the compressor is increased. This improves the compressor's energy efficiency during high-frequency operation, adapting to the operating requirements of the compressor at 72Hz and above.

[0056] Reference Figure 2As shown in the embodiment of the present invention, on the projection plane perpendicular to the thickness direction of the valve plate 200, the edge of the free segment 223 includes an arc-shaped edge segment 2231, the center point of the arc-shaped edge segment 2231 is point O, the center point of the line connecting the two sides at the maximum width of the fixed segment 221 is point A, and the line connecting point O and point A is defined as the second reference line L2. The projection of either the outer edge or the inner edge of the tongue spring 220 intersects with the second reference line L2. With this scheme, the structural asymmetry of the tongue spring 220 is improved, the eccentric opening effect of the free segment 223 is more obvious, the opening angle is increased, and thus the air intake volume in each intake stroke is increased.

[0057] Reference Figure 2 and Figure 3 As shown, in the embodiment of the present invention, the first edge segment 2222, the second edge segment 2221, the third edge segment 2212 and the fourth edge segment 2211 are respectively constructed as straight edges, the included angle between the second edge segment 2221 and the fourth edge segment 2211 is θ, and the included angle between the first edge segment 2222 and the third edge segment 2212 is β, satisfying: θ≤β.

[0058] Understandably, the fourth edge segment 2211 and the second edge segment 2221 reflect the extension directions of the fixed segment 221 and the swing arm segment 222 on their outer edges, respectively, while the third edge segment 2212 and the first edge segment 2222 reflect the extension directions of the fixed segment 221 and the swing arm segment 222 on their inner edges, respectively. On the outer edge side, the angle θ between the fourth edge segment 2211 and the second edge segment 2221 is relatively small, indicating a greater degree of bending between the outer edges of the fixed segment 221 and the swing arm segment 222, and a greater extent of expansion of the fixed segment 221 away from the swing arm segment 222 on its outer side. On the inner edge side, the angle β between the third edge segment 2212 and the first edge segment 2222 is relatively large, indicating a smaller degree of bending between the inner edges of the fixed segment 221 and the swing arm segment 222, and a smoother transition between the two on the inner side.

[0059] Therefore, the turning angle of the outer edge of the tongue spring 220 is smaller, and the material at the outer edge is more strongly constrained by bending; the turning angle of the inner edge is larger and gentler, and the bending constraint at the inner edge is relatively weaker. The inner side of the tongue spring 220 is the side facing the other tongue spring 220, and the outer side is the side away from the other tongue spring 220. This results in a greater lifting amplitude on the inner side of the free section 223 when it is pushed open by the refrigerant pressure difference, which in turn increases the opening of the tongue spring 220. That is, the direction of the fixed section 221 and the swing arm section 222 changes → the turning amplitude of the inner edge is smaller → the equivalent bending stiffness of the inner side is reduced → the deformation of the inner side is greater under the same pressure difference → the inner side of the free section 223 is lifted higher → the tilting and flipping amplitude is greater → the maximum opening is greater → the flow area is increased → the air intake volume is increased.

[0060] The angular relationship θ≤β causes the distance between the outer and inner edges of the fixed section 221 to gradually increase along the direction away from the swing arm section 222, meaning the fixed section 221 has a larger width closer to its root. This increased root width of the fixed section 221 increases the moment of inertia at the connection between the fixed section 221 and the inner wall of the notch 214, improving bending stiffness and overall strength. During high-frequency compressor operation, when the compression stroke begins, the free section 223 needs to quickly close the suction port 110 under the rebound force of the tongue spring 220. Higher root stiffness of the fixed section 221 results in faster rebound speed of the tongue spring 220, shorter closing time of the suction port 110 by the free section 223, reduced refrigerant return flow, and increased effective suction volume of the compressor, thereby improving the compressor's energy efficiency under high-frequency operating conditions.

[0061] Reference Figure 2 and Figure 3 As shown in the embodiment of the present invention, the bending ratio of the tongue spring 220 is defined as S, S=θ / β, satisfying: 0.7≤S≤0.86. The bending ratio S reflects the degree of geometric asymmetry of the tongue spring 220 between the fixed section 221 and the swing arm section 222. The smaller the S value, the smaller θ is relative to β, the greater the bending degree of the outer edge relative to the inner edge, the more obvious the width expansion at the root of the fixed section 221, and the higher the asymmetry of the tongue spring 220; the larger the S value, the closer θ is to β, the more consistent the bending degree of the inner and outer edges of the fixed section 221, and the closer the tongue spring 220 is to symmetry.

[0062] When S is less than 0.7, θ is too small relative to β. This indicates that the outward expansion of the outer edge of the fixed section 221 is too large, or the transition between the inner edge of the swing arm section 222 and the inner edge of the fixed section 221 is too gentle, resulting in an excessively large cross-sectional width at the root of the fixed section 221 and excessively high bending stiffness. Although the high stiffness can ensure the rebound speed of the tongue spring 220, the excessive stiffness makes the constraint force on the free section 223 too strong during the intake stroke. The gas pressure difference is insufficient to push the free section 223 open to a sufficient angle, reducing the opening of the free section 223. The effective flow area of ​​the intake port 110 is insufficient, resulting in a reduction in the amount of refrigerant entering the cylinder during each intake stroke and insufficient intake volume.

[0063] When S is greater than 0.86, θ is too large relative to β. This indicates that the outer edge of the fixed section 221 is not sufficiently extended, or the inner edge of the swing arm section 222 is bent too much, resulting in a smaller cross-sectional width at the root of the fixed section 221 and insufficient bending stiffness. Insufficient stiffness directly affects the rebound speed of the tongue spring 220. At the beginning of the compression stroke, the free section 223 cannot return to its initial position to close the suction port 110 in a short time. Some refrigerant flows back from the suction port 110 to the suction side, increasing the backflow and reducing the effective intake volume, thus lowering the compressor's energy efficiency.

[0064] By controlling S within the range of 0.7 to 0.86, the width and stiffness of the root of the fixed section 221 are within a reasonable range. On the one hand, the fixed section 221 has sufficient strength to ensure the rebound speed of the tongue spring 220, allowing the free section 223 to quickly close the intake port 110 at the beginning of the compression stroke, reducing refrigerant backflow. On the other hand, the stiffness of the fixed section 221 is not too high, and the swing arm section 222 maintains sufficient flexibility, allowing the free section 223 to open to a suitable angle during the intake stroke, ensuring sufficient air intake.

[0065] Reference Figure 2 and Figure 3 As shown, in the embodiment of the present invention, the included angle θ between the fourth edge segment 2211 and the second edge segment 2221 satisfies: 95°≤θ≤140°. The included angle β between the third edge segment 2212 and the first edge segment 2222 satisfies: 135°≤β≤170°.

[0066] When θ is less than 95°, the bending angle between the fourth edge segment 2211 and the second edge segment 2221 is too large, and the outward expansion of the outer edge of the fixed segment 221 is too large, resulting in an excessively large cross-sectional width at the root of the fixed segment 221. This excessive cross-sectional width leads to excessively high bending stiffness in the fixed segment 221, causing the free segment 223 to be overly constrained during the intake stroke, limiting its opening angle, reducing its opening size, and resulting in insufficient effective flow area of ​​the intake port 110 and insufficient intake volume. When θ is greater than 140°, the bending angle between the fourth edge segment 2211 and the second edge segment 2221 is too small, the outward expansion of the outer edge of the fixed segment 221 is insufficient, the cross-sectional width at the root of the fixed segment 221 is too small, resulting in insufficient stiffness, slow rebound speed of the tongue spring 220, and the free segment 223 failing to quickly close the intake port 110 at the start of the compression stroke. This increases the refrigerant return flow, reduces the effective intake volume, and lowers the compressor's energy efficiency. With θ set within the range of 95° to 140°, the width distribution on the outer side of the fixed section 221 is within a reasonable range, taking into account both the rebound speed and the opening angle.

[0067] When β is greater than 170°, the third edge segment 2212 and the first edge segment 2222 almost form a flat angle. The transition between the inner edge of the fixed segment 221 and the inner edge of the swing arm segment 222 is extremely smooth, with almost no bending on the inner edge. This results in an excessively wide width at the root of the fixed segment 221 in the inner direction. Combined with the outer side, this leads to an excessively large overall cross-sectional width and high stiffness of the fixed segment 221, limiting the opening of the free segment 223 and resulting in insufficient air intake. When β is less than 135°, the bending angle between the third edge segment 2212 and the first edge segment 2222 is too large. The inner edge of the fixed segment 221 contracts inward too much, and the width of the swing arm segment 222 changes too drastically in the area near the fixed segment 221. This results in a smaller width at the root of the fixed segment 221, insufficient stiffness, and slow rebound speed. Furthermore, the uneven width variation of the swing arm segment 222 easily leads to stress concentration at the bending point. With β set in the range of 135° to 170°, the width distribution inside the fixed segment 221 is within a reasonable range.

[0068] By setting θ to 95° to 140° and β to 135° to 170°, the width gradient distribution of the fixed section 221 and the swing arm section 222 is reasonable, the root stiffness of the fixed section 221 is moderate, the flexibility of the swing arm section 222 is appropriate, and the tongue spring 220 has the ability to close quickly and open sufficiently under high-frequency operating conditions.

[0069] Reference Figure 2 and Figure 3 As shown, in an embodiment of the present invention, the fourth edge segment 2211 and the second edge segment 2221 are connected by a first arc-shaped segment 224. The third edge segment 2212 and the first edge segment 2222 are connected by a second arc-shaped segment 225. By providing a first arc-shaped segment 224 between the fourth edge segment 2211 and the second edge segment 2221 for the transition connection, the sharp corner of the outer edge is transformed into a smooth arc transition. The arc transition makes the cross-sectional change between the outer edge of the fixed segment 221 and the outer edge of the swing arm segment 222 in the connection area more gradual, the stress is evenly distributed along the curvature direction of the arc segment, and the local stress peak is reduced. Similarly, by providing a second arc-shaped segment 225 between the third edge segment 2212 and the first edge segment 2222 for the transition connection, the sharp corner of the inner edge is also transformed into a smooth arc transition, reducing the stress concentration in the inner connection area, reducing the local stress amplitude under fatigue load, and improving the fatigue life and operational reliability of the tongue spring 220 under long-term high-frequency operation conditions.

[0070] Reference Figure 2 and Figure 3As shown in the embodiment of the present invention, part of the edge of the free segment 223 is constructed as an arc-shaped edge segment 2231, and another part of the edge of the free segment 223 is constructed as a transition edge segment 2232. The transition edge segment 2232 is arc-shaped and connected to the first edge segment 2222. The outer edge of the swing arm segment 222 includes a second edge segment 2221, which is tangent to the edge of the free segment 223.

[0071] From the perspective of the asymmetry of the tongue spring 220, the swing arm segment 222 is connected to the side of the free segment 223 away from the other free segment 223. The second edge segment 2221 extends from the outer edge of the swing arm segment 222 to the arc edge segment 2231 of the free segment 223, and the two form a tangential connection on the outside of the free segment 223. Since the swing arm segment 222 is located on the outside of the free segment 223, and the second edge segment 2221 extends in a straight line and is tangent to the arc edge segment 2231 of the free segment 223, the constraint effect of the swing arm segment 222 on the free segment 223 is concentrated at the tangent point on the outer side of the arc edge segment 2231 of the free segment 223. This connection method causes the point of application of the constraint force of the swing arm segment 222 to deviate from the geometric center of the free segment 223 and be located in the outer region of the free segment 223, further enhancing the asymmetry of the tongue spring 220.

[0072] When the free segment 223 tilts upwards due to the gas pressure difference during the intake stroke, the swing arm segment 222 constrains the free segment 223 through the tangential connection point between the second edge segment 2221 and the arc edge segment 2231. Since the constraint force acts on the outer side of the free segment 223, the constraint on the inner side is less, resulting in a greater tilting amplitude on the inner side than the outer side, creating an eccentric opening effect. The tangential connection ensures a smooth geometric transition between the swing arm segment 222 and the free segment 223. During the eccentric opening process, the force transmission path is continuous, preventing local stress concentration or motion interference due to geometrical abrupt changes at the connection point. The free segment 223 can smoothly eccentrically swing, increasing the opening angle, increasing the effective flow area of ​​the intake port 110, and improving the intake volume in each intake stroke.

[0073] Reference Figure 2 and Figure 3 As shown, in an embodiment of the present invention, the valve body 100 is provided with a first exhaust port 120, which is located on one side of the two intake ports 110 along the first direction. The body 210 is provided with a second exhaust port 211, which is located between the two tongue springs 220, and the second exhaust port 211 and the first exhaust port 120 are connected.

[0074] During the operation of a reciprocating compressor, the piston reciprocates within the cylinder, alternating between the intake and compression / exhaust strokes. During the intake stroke, the piston moves away from the valve body 100, creating a negative pressure within the cylinder, allowing refrigerant gas to enter through the two intake ports 110. During the compression / exhaust stroke, the piston moves towards the valve body 100, compressing the refrigerant gas within the cylinder. When the pressure within the cylinder rises above the exhaust pressure, the compressed, high-pressure refrigerant gas must be discharged from the cylinder.

[0075] The valve body 100 has a first exhaust port 120 located on one side of the two intake ports 110 along the first direction. The valve plate 200 has a second exhaust port 211 located in the area between the two tongue springs 220. The second exhaust port 211 and the first exhaust port 120 are connected to form an exhaust passage. During the compression and exhaust stroke, the high-pressure refrigerant gas in the cylinder is discharged from the cylinder through the first exhaust port 120 on the valve body 100 and the second exhaust port 211 on the valve plate 200 body 210, and enters the exhaust-side pipeline.

[0076] The first exhaust port 120 is located on one side of the two intake ports 110 along the first direction, occupying an independent area on the valve body 100, thus spatially separating the exhaust and intake channels and preventing interference from the high-pressure refrigerant to the intake side during exhaust. The second exhaust port 211 is located between the two tongue springs 220, utilizing the space between them to arrange the exhaust channel, resulting in a compact arrangement of the exhaust and intake functional areas on the valve plate 200 and improving the space utilization of the valve plate 200. The second exhaust port 211 is connected to the first exhaust port 120, ensuring unobstructed exhaust channels and allowing the compressed refrigerant gas to be smoothly discharged from the cylinder, maintaining the normal intake and exhaust cycle of the compressor.

[0077] Reference Figure 1 and Figure 2 As shown, in an embodiment of the present invention, the body 210 includes a filling sheet 230, which is disposed between two tongue springs 220. The filling sheet 230 is provided with a second vent hole 211. Along a second direction perpendicular to the first direction, the width of the filling sheet 230 along the first direction gradually increases, then gradually decreases, and then gradually increases again.

[0078] The filler plate 230, located between the two tongue springs 220, is a component of the body 210. A second vent hole 211 is provided on the filler plate 230, which communicates with the first vent hole 120 on the valve body 100 to form an venting channel. Viewed along the second direction, the width of the filler plate 230 along the first direction exhibits a gradual increase, then a gradual decrease, and then a gradual increase again. This width variation matches the shape of the gap between the two tongue springs 220. The gradual rather than abrupt change in the width of the filler plate 230 along the second direction ensures a uniform gap between the edge contour of the filler plate 230 and the outer contour of the tongue springs 220. This uniform gap ensures that the two tongue springs 220 do not interfere with the filler plate 230 during opening and closing, and the oscillating movement of the tongue springs 220 is unimpeded.

[0079] Understandably, in the region where the two free segments 223 are close to each other, the distance between them is small, and the width of the filler plate 230 is correspondingly narrower in this region. Extending along the second direction towards the swing arm segment 222, the two swing arm segments 222 move inwards, and the distance between them first changes and then widens again. The width of the filler plate 230 then first increases, then decreases, and then increases again, conforming to the contour of the gap between the two tongue springs 220. By filling the gap between the two tongue springs 220, the filler plate 230 reduces the clearance volume, thereby reducing the amount of residual gas, increasing the effective intake stroke, and improving the intake volume.

[0080] Reference Figure 2 As shown, in an embodiment of the present invention, two springs 220 are arranged symmetrically along an axis of symmetry, which is perpendicular to the first direction. It is understood that during the suction stroke of the reciprocating compressor, a negative pressure is formed inside the cylinder, and refrigerant gas simultaneously enters the cylinder from both suction ports 110. The two springs 220 open simultaneously under the influence of the gas pressure difference. The symmetrical arrangement ensures that the two springs 220 have the same geometric parameters and material distribution, thus their bending stiffness, resilience, and motion characteristics are consistent. Under the same gas pressure difference, the two springs 220 open at the same angle, and their opening and closing times are consistent. The flow state of the two suction ports 110 remains synchronized, which is beneficial for improving the overall service life and reliability of the suction valve assembly 1000.

[0081] Reference Figure 1 As shown, in an embodiment of the present invention, the valve body 100 is provided with a plurality of first mounting holes 130, and the valve plate 200 is provided with a plurality of second mounting holes 212 corresponding to the positions of the first mounting holes 130, so that the valve plate 200 can be connected to the valve body 100 by passing through the first mounting holes 130 and the second mounting holes 212 with a plurality of fasteners such as screws and bolts.

[0082] A compressor according to one embodiment of the present invention includes the suction valve assembly 1000 of the above embodiment. The compressor of this embodiment uses the suction valve assembly 1000 of the above embodiment, with a valve body 100 and a valve plate 200 connected. Two springs 220 of the valve plate 200 are connected to the notch 214 of the body 210 via a fixed section 221. The free section 223 of the springs 220 can cover the suction port 110 on the valve body 100. Therefore, when the compressor draws air, the free section 223 opens the suction port 110, and when it discharges air, the free section 223 closes the suction port 110. Since there are two springs 220 and two suction ports 110, the suction volume is larger than that of a single-port design. Therefore, by increasing the overall strength of the springs 220, the rebound speed of the springs 220 can be increased, resulting in a faster response speed to close the suction port 110, thereby reducing the backflow and improving the energy efficiency of the compressor. To increase the opening of the reed 220, the distance between the two first edge segments 2222 is gradually reduced or kept constant, the distance between the two second edge segments 2221 is gradually reduced or kept constant, the distance between the two third edge segments 2212 is gradually increased, and the distance between the two fourth edge segments 2211 is gradually increased. Therefore, when the free segment 223 is tilted up under pressure, the free segment 223 opens eccentrically, which can increase the opening angle of the free segment 223 to a certain extent, thereby increasing the intake volume.

[0083] Since the compressor adopts all the technical solutions of the suction valve group 1000 of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be repeated here.

[0084] A refrigeration device according to one embodiment of the present invention includes the compressor described in the above embodiments. The refrigeration device can be a refrigerator, freezer, medicine cabinet, display cabinet, wine cabinet, etc. The refrigeration device of this embodiment uses the compressor described in the above embodiments. A valve body 100 and a valve plate 200 are connected. Two springs 220 of the valve plate 200 are connected to a notch 214 in the body 210 via a fixed section 221. The free section 223 of the springs 220 can cover the suction port 110 on the valve body 100. Therefore, when the compressor draws in air, the free section 223 opens the suction port 110, and when it discharges air, the free section 223 closes the suction port 110. Since there are two springs 220 and two suction ports 110, the air intake is greater than that of a single-port design. Therefore, by increasing the overall strength of the springs 220, the rebound speed of the springs 220 can be increased, resulting in a faster response speed to close the suction port 110, thereby reducing the backflow and improving the energy efficiency of the compressor. To increase the opening of the reed 220, the distance between the two first edge segments 2222 is gradually reduced or kept constant, the distance between the two second edge segments 2221 is gradually reduced or kept constant, the distance between the two third edge segments 2212 is gradually increased, and the distance between the two fourth edge segments 2211 is gradually increased. Therefore, when the free segment 223 is tilted up under pressure, the free segment 223 opens eccentrically, which can increase the opening angle of the free segment 223 to a certain extent, thereby increasing the intake volume.

[0085] Since the refrigeration equipment adopts all the technical solutions of the compressor in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments, which will not be repeated here.

[0086] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. An intake valve assembly, characterized in that, include: The valve body is provided with two air intake holes arranged along the first direction; A valve plate is connected to the valve body. The valve plate includes a body and two tongue springs. The body has a notch. The two tongue springs are respectively disposed in the notch and arranged along the first direction. The tongue springs include a fixed section, a swing arm section and a free section connected in sequence. The fixed section is fixedly connected to the inner wall of the notch. The free section is configured to swing relative to the body and cover the corresponding air intake hole. Wherein, each of the swing arm segments includes a first edge segment on the side facing the other swing arm segment, the first edge segment being connected to the edge of the free segment; each of the swing arm segments includes a second edge segment on the side facing away from the other swing arm segment; each of the fixed segments includes a third edge segment on the side facing the other fixed segment; and each of the fixed segments includes a fourth edge segment on the side facing away from the other fixed segment. Along a second direction perpendicular to the first direction, the distance between two first edge segments gradually decreases or remains constant, the distance between two second edge segments gradually decreases or remains constant, the distance between two third edge segments gradually increases, and the distance between two fourth edge segments gradually increases.

2. The intake valve assembly according to claim 1, characterized in that: Along a direction away from the free segment, the distance between the first edge segment and the second edge segment gradually decreases; or, Along a direction away from the free segment, the first edge segment gradually approaches the second edge segment.

3. The intake valve assembly according to claim 1, characterized in that: Along a direction away from the swing arm segment, the distance between the third edge segment and the fourth edge segment gradually increases; or, Along a direction away from the swing arm segment, the third edge segment gradually moves away from the fourth edge segment.

4. The intake valve assembly according to claim 1, characterized in that: On the projection plane perpendicular to the thickness direction of the valve plate, the edge of the free segment includes an arc edge segment, the center point of the arc edge segment is point O, and the straight line passing through point O and perpendicular to the first direction is defined as the first reference line L1. The end of the first edge segment facing the free segment and the end of the second edge segment facing the free segment are respectively located on the side of the first reference line L1 away from the other tongue.

5. The intake valve assembly according to claim 1, characterized in that: On the projection plane perpendicular to the thickness direction of the valve plate, the edge of the free segment includes an arc edge segment, the center point of the arc edge segment is point O, the center point of the line connecting the two sides at the maximum width of the fixed segment is point A, the line connecting point O and point A is defined as the second reference line L2, and the projected outer contour line of the tongue spring intersects with the second reference line L2.

6. The intake valve assembly according to claim 1, characterized in that: The first edge segment, the second edge segment, the third edge segment, and the fourth edge segment are each constructed as straight edges. The included angle between the second edge segment and the fourth edge segment is θ, and the included angle between the first edge segment and the third edge segment is β, satisfying: θ≤β.

7. The intake valve assembly according to claim 6, characterized in that: The bending ratio of the tongue spring is defined as S, where S = θ / β, satisfying: 0.7 ≤ S ≤ 0.

86.

8. The intake valve assembly according to claim 6, characterized in that: The included angle θ between the second edge segment and the fourth edge segment satisfies: 95° ≤ θ ≤ 140°; and / or, The included angle β between the first edge segment and the third edge segment satisfies: 135°≤β≤170°.

9. The intake valve assembly according to claim 6, characterized in that: The second edge segment and the fourth edge segment are connected by a first arc-shaped segment; and / or, The first edge segment and the third edge segment are connected by a second arc segment.

10. The intake valve assembly according to claim 1, characterized in that: The edge of the free segment includes a circular arc edge segment, and the second edge segment is tangent to the circular arc edge segment.

11. The intake valve assembly according to claim 1, characterized in that: The two tongue reeds are arranged symmetrically along an axis of symmetry, which is perpendicular to the first direction.

12. A compressor, characterized in that: Includes the intake valve assembly as described in any one of claims 1 to 11.

13. A refrigeration device, characterized in that: Includes the compressor described in claim 12.

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