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 body and a valve block, the valve body is connected with the valve block, two reeds of the valve block are connected into the notch of the body through fixed sections, and the free sections of the reeds cover the air suction holes of the valve body. Therefore, the free section opens the suction hole when the compressor sucks air and closes the suction hole when the compressor exhausts air. 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, and the energy efficiency of the compressor can be improved. Due to the fact that the minimum widths of the swing arm sections of the two reeds are different, the opening resistances of the two reeds are different, and the situation that the air suction holes are opened and closed in sequence exists. Therefore, the two reeds with different minimum widths are respectively arranged in the embodiment, so that the operation requirements of the compressor at high frequency and low frequency are considered, and the opening resistance of the reeds can be reduced while the air suction amount can be improved to a certain extent.

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] Refrigerators employ reciprocating compressors with an intake valve assembly. When the piston draws in refrigerant, the reed of the intake valve assembly opens the intake port to draw in the refrigerant; when the piston discharges refrigerant, the reed closes the intake port. When the compressor operates at high frequencies of 72Hz and above, the effective intake volume is of paramount importance, and this effective intake volume is related to the reed's rebound speed. If the reed's rebound speed is too slow, the refrigerant already drawn into the cylinder will be pushed back into the intake chamber by the piston during the initial compression phase, increasing the backflow and reducing the effective intake volume. To improve the reed's rebound speed, the reed is typically designed with a heavier head and wider arms to increase stiffness and improve rebound speed. However, increasing the reed's stiffness leads to increased opening resistance. When the compressor operates at low frequencies of 27Hz and below, the compressor's efficiency is of paramount importance, and efficiency is related to the reed's opening resistance. A reed with excessively high stiffness requires a greater pressure differential to be pushed open, resulting in a slower opening speed of the reed during the initial intake phase, a shorter effective intake time, and insufficient intake volume. It also increases the power consumption of the compressor. Therefore, the reed technology of this type is difficult to balance the needs of the compressor in different modes. 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 effective intake volume while reducing the opening resistance of the reed valve.

[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. One end of 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, the minimum width of one of the tongue springs in the swing arm section is H, and the minimum width of the other tongue spring in the swing arm section is h, satisfying: H > h.

[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 springs of the valve plate are connected to the notch in the body via a fixed section, and the free section of the spring covers the intake port of the valve body. Therefore, the free section opens the intake port when the compressor draws in air and closes the intake port when it discharges air. Since there are two springs and two intake ports, the intake volume is larger than that of a single-port design, improving the compressor's energy efficiency. Because the minimum widths of the swing arm sections of the two springs are different, the opening resistance of the two springs is different, resulting in the possibility of the intake ports opening and closing sequentially. The spring with a minimum width of H has a faster rebound speed, reducing backflow and increasing the effective intake volume, which is beneficial for improving the compressor's energy efficiency during high-frequency operation; however, its opening resistance is relatively larger than that of the spring with a minimum width of h. The spring with a minimum width of h has lower opening resistance, which is beneficial for improving the compressor's efficiency during low-frequency operation, but its rebound speed is slower than that of the spring with a minimum width of H, resulting in a reduced effective intake volume. Therefore, this embodiment is equipped with two tongue reeds with different minimum widths to take into account the operating requirements of the compressor at both high and low frequencies. This can increase the intake volume to a certain extent while reducing the opening resistance of the tongue reeds.

[0007] According to some embodiments of the present invention, the tongue spring with a minimum width of H of the swing arm segment is a first tongue spring, and at least a portion of the outer edge of the free segment of the first tongue spring is constructed as a first arc segment with a radius of R. The tongue spring with a minimum width of h in the swing arm section is a second tongue spring, and at least a portion of the outer edge of the free section of the second tongue spring is constructed as a second arc segment with a radius of r. It satisfies: 0.7≤(H / R²) / (h / r²)≤2.3.

[0008] According to some embodiments of the present invention, the radius R of the first arc segment and the radius r of the second arc segment satisfy: R ≥ r.

[0009] According to some embodiments of the present invention, the minimum width of one of the swing arm segments is H, and the minimum width of the other swing arm segment is h, satisfying: 1.4≤H / h≤2.4.

[0010] According to some embodiments of the present invention, the width of the swing arm segment gradually decreases and then gradually increases along a second direction perpendicular to the first direction.

[0011] According to some embodiments of the present invention, the width of the fixed segment gradually increases along a second direction perpendicular to the first direction.

[0012] According to some embodiments of the present invention, the side of the fixed section and the swing arm section facing the other tongue spring is the inner edge, and the side of the fixed section and the swing arm section away from the other tongue spring is the outer edge; Along the direction from the free segment to the fixed segment, the inner edge includes a first edge segment, a second edge segment, and a third edge segment connected in sequence, and the outer edge includes a fourth edge segment and a fifth edge segment connected in sequence; In a second direction perpendicular to the first direction, the two first edge segments extend in directions away from each other, the two second edge segments extend in directions close to each other, and the distance between the two third edge segments remains unchanged; the two fourth edge segments extend in directions close to each other, and the two fifth edge segments extend in directions away from each other.

[0013] According to some embodiments of the present invention, the swing arm segment has a first edge segment and a fourth edge segment, and the fixed segment has a second edge segment, a third edge segment and a fifth edge segment.

[0014] According to some embodiments of the present invention, the first edge segment, the second edge segment, the fourth edge segment and the fifth edge segment are respectively constructed as arc segments, and the third edge segment is constructed as a straight edge.

[0015] According to some embodiments of the present invention, the valve body is provided with a first vent hole, and the body further includes a filler piece located between the two tongue springs, the filler piece and the tongue springs are spaced apart and provided with a second vent hole, the second vent hole and the first vent hole are in communication.

[0016] According to some embodiments of the present invention, the two tongue reeds are arranged symmetrically with respect to the second 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 suction valve assembly of the first aspect embodiment, the suction 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, and the free sections of the springs cover the suction port of the valve body. Therefore, the free section opens the suction port when the compressor draws in air and closes the suction port when it discharges air. Since there are two springs and two suction ports, the suction volume is larger than that of a single-port design, improving the compressor's energy efficiency. Because the minimum widths of the swing arm sections of the two springs are different, the opening resistances of the two springs are different, resulting in situations where the suction ports open and close sequentially. The spring with a minimum width of H has a faster rebound speed, reducing backflow and increasing the effective suction volume, which is beneficial for improving the compressor's energy efficiency during high-frequency operation; however, its opening resistance is relatively larger than that of the spring with a minimum width of h. The spring with a minimum width of h has lower opening resistance, which is beneficial for improving the compressor's efficiency during low-frequency operation, but its rebound speed is slower than that of the spring with a minimum width of H, resulting in a reduced effective suction volume. Therefore, this embodiment is equipped with two tongue reeds with different minimum widths to take into account the operating requirements of the compressor at both high and low frequencies. This can increase the intake volume to a certain extent while reducing the opening resistance of the tongue reeds.

[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 suction valve assembly is connected by a valve body and valve plates. Two springs on the valve plates are connected to a notch in the body via a fixed section, and the free sections of the springs cover the suction port of the valve body. Therefore, the free section opens the suction port when the compressor draws in air and closes it when it discharges air. Since there are two springs and two suction ports, the suction volume is larger than that of a single-port design, improving the compressor's energy efficiency. Because the minimum widths of the swing arm sections of the two springs are different, the opening resistances of the two springs are different, resulting in situations where the suction ports open and close sequentially. The spring with a minimum width of H has a faster rebound speed, reducing backflow and increasing the effective suction volume, which is beneficial for improving the compressor's energy efficiency during high-frequency operation; however, its opening resistance is relatively larger than that of the spring with a minimum width of h. The spring with a minimum width of h has lower opening resistance, which is beneficial for improving the compressor's efficiency during low-frequency operation, but its rebound speed is slower than that of the spring with a minimum width of H, resulting in a reduced effective suction volume. Therefore, this embodiment is equipped with two tongue reeds with different minimum widths to take into account the operating requirements of the compressor at both high and low frequencies. This can increase the intake volume to a certain extent while reducing the opening resistance of the tongue reeds.

[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 symmetrical dual-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 symmetrical dual-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; swing arm section 222; free section 223; inner edge 226; first edge section 2261; second edge section 2262; third edge section 2263; outer edge 227; fourth edge section 2271; fifth edge section 2272; filler plate 230; First reed 240; First arc segment 241; Second tongue reed 250; second circular arc segment 251. 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 opposite 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. In this process, the opening and closing of the reed valve directly affects the compressor's suction volume and efficiency. When the compressor operates at high frequencies of 72Hz and above, the effective suction volume is more important, while when the compressor operates at low frequencies of 27Hz and below, the compressor efficiency, i.e., the ratio of effective suction volume to compression work, is more important. The compression work, in turn, is related to the opening resistance of the reed valve.

[0029] To balance the compressor's performance at high and low frequencies, 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 refrigerator compressor, such as a reciprocating compressor. The intake valve assembly 1000 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. The valve plate 200 includes a body 210 and two springs 220. The body 210 has a notch 214. The two springs 220 are respectively disposed in the notch 214 and arranged along the first direction. The springs 220 include 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. 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 cover the corresponding intake hole 110. Among them, the minimum width of one tongue spring 220 in the swing arm section 222 is H, and the minimum width of the other tongue spring 220 in the swing arm section 222 is h, satisfying: H > h.

[0030] The swing arm section 222 of the tongue spring 220 is the transition area connecting the fixed section 221 and the free section 223. The width of the swing arm section 222 determines the bending stiffness of the tongue spring 220. The wider the swing arm section 222, the greater the moment of inertia of the section, and the higher the bending stiffness of the tongue spring 220; the narrower the swing arm section 222, the lower the bending stiffness. The bending stiffness affects the pressure difference required for the tongue spring 220 to be pushed open by the refrigerant, i.e., the opening resistance; it also affects the time required for the tongue spring 220 to fall back from the maximum lift position to the closed position, i.e., the rebound speed.

[0031] When the compressor operates at high frequency (4320 r / min and above), the piston reciprocating cycle is short, leaving a limited time window for the reed 220 to complete the three actions of opening, intake, and closing. If the reed 220 is not closed when the piston begins to compress, some of the refrigerant already drawn into the cylinder will be pushed back into the intake chamber by the piston, forming a backflow. The effective intake volume under high-frequency conditions equals the absolute intake volume minus the backflow; therefore, the rebound speed has a significant impact on the effective intake volume at high frequencies. To reduce the backflow, the reed 220 needs to have high stiffness to accelerate the rebound. However, if the stiffness of both reeds 220 is designed to be high, the opening resistance of both reeds 220 will be too high under low-frequency conditions, increasing the compressor's power consumption and decreasing its efficiency.

[0032] Reference Figure 4 As shown, Figure 4 The bar chart reflects the improvement in compressor performance during high-frequency operation brought about by the intake valve assembly 1000 in this embodiment. The left side shows the traditional symmetrical dual-valve structure, which is a scheme with two symmetrically arranged springs and a minimum width of h for the swing arm section; the right side shows the scheme 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 102.4, which is an improvement of approximately 2.4% compared to the symmetrical scheme.

[0033] 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 return flow has a relatively small impact on the effective intake volume. Under low-frequency conditions, compressor efficiency is the primary concern, and efficiency is negatively correlated with the opening resistance of the reed 220. Lower opening resistance means the reed 220 is pushed open faster during the initial intake phase, resulting in a longer effective intake time and less work required to push it open. However, if the stiffness of both reeds 220 is designed to be low, the rebound speed of both reeds 220 will be slow under high-frequency conditions, increasing the return flow and resulting in insufficient effective intake volume.

[0034] Reference Figure 5 As shown, Figure 5The 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 symmetrical dual-valve structure, where two springs are symmetrically arranged and the minimum width of the swing arm section is H. The right side shows the design of this embodiment. Low-frequency capability refers to the effective intake volume / compression work. Using the high-frequency capability of the single-valve structure as a baseline of 1, the high-frequency capability of this embodiment is 1.003, and the low-frequency capability is improved by approximately 0.3% compared to the symmetrical design.

[0035] In this embodiment, the minimum widths of the swing arm sections 222 of the two tongue springs 220 are designed to be different values ​​H and h, with H being greater than h, giving the two tongue springs 220 different bending stiffnesses. The tongue spring 220 with a minimum width of H in its swing arm section 222 has higher stiffness and a faster rebound speed during high-frequency operation. The free section 223 can close the corresponding intake port 110 before the piston enters the compression stroke, reducing the backflow corresponding to that intake port 110. The tongue spring 220 with a minimum width of h in its swing arm section 222 has lower stiffness and lower opening resistance. During low-frequency operation, it can be pushed open under a small intake pressure difference, resulting in a faster opening speed, a longer effective intake time, and less work required to push open the tongue spring 220, which helps reduce the power consumption of the compressor.

[0036] During high-frequency operation, the spring 220 with a minimum width of h in the swing arm section 222 has lower stiffness and a higher lift than the spring 220 with a minimum width of H in the swing arm section 222 under the same gas pressure difference. A higher lift results in a larger flow area between the free section 223 and the intake port 110, leading to a larger amount of refrigerant flowing through per unit time. Therefore, the absolute intake volume of the intake port 110 corresponding to the spring 220 with a minimum width of h in the swing arm section 222 is greater than that corresponding to the spring 220 with a minimum width of H in the swing arm section 222. Although the spring 220 with a minimum width of h in the swing arm section 222 has a slower closing speed due to its higher lift and longer rebound stroke, and its corresponding return flow is also larger, the combined effective intake volume of the two springs 220 is equal to the sum of the absolute intake volumes of the two intake ports 110 minus the sum of the return flow rates of the two intake ports 110. The tongue spring 220 with a minimum width of H in the swing arm section 222 is responsible for reducing the backflow, while the tongue spring 220 with a minimum width of h in the swing arm section 222 is responsible for increasing the absolute intake volume. The two work together to make the total effective intake volume higher than the symmetrical design scheme in which both tongue springs 220 adopt the same stiffness.

[0037] During low-frequency operation, due to the long piston reciprocating cycle, both reeds 220 have sufficient time to close, resulting in relatively small return flows. The reed 220 with a minimum width of h in the swing arm section 222 experiences low opening resistance and is pushed open early in the intake process, reducing power consumption. The total intake volume of both intake ports 110 meets the requirements under low-frequency conditions, while the overall opening resistance decreases due to the reduced stiffness of one reed 220, thus improving compressor efficiency.

[0038] Through the above asymmetrical design, the two tongue springs 220 can each play their advantages under different frequency operating conditions: the tongue spring 220 with a minimum width of H in the swing arm section 222 tends to reduce the high frequency return flow, while the tongue spring 220 with a minimum width of h in the swing arm section 222 tends to increase the absolute intake volume in the high frequency and reduce the opening resistance in the low frequency, so that the intake valve assembly 1000 can simultaneously adapt to the operating requirements of the compressor in both low and high frequencies.

[0039] Reference Figure 2 and Figure 3 As shown, in an embodiment of the present invention, the tongue spring 220 with a minimum width of H in the swing arm segment 222 is a first tongue spring 240. At least a portion of the outer edge 227 of the free segment 223 of the first tongue spring 240 is constructed as a first arc segment 241, and the radius of the first arc segment 241 is R. The tongue spring 220 with a minimum width of h in the swing arm segment 222 is a second tongue spring 250. At least a portion of the outer edge 227 of the free segment 223 of the second tongue spring 250 is constructed as a second arc segment 251, and the radius of the second arc segment 251 is r, satisfying: 0.7 ≤ (H / R²) / (h / r²) ≤ 2.3. For example, the value of (H / R²) / (h / r²) can be 0.7, 0.9, 1, 1.5, 2, 2.3, etc.

[0040] The radius R of the first arc segment 241 and the radius r of the second arc segment 251 represent the outer contour dimensions of the free segments 223 of the first and second springs 240 and 250, respectively. The larger the outer contour dimension of the free segment 223, the larger the area covered by the free segment 223 over the intake hole 110, and the greater the mass of the free segment 223. The mass of the free segment 223 affects the dynamic response characteristics of the spring 220: the greater the mass, the greater the inertia of the spring 220 during opening and closing, thus affecting both opening resistance and rebound time.

[0041] The parameter (H / R²) / (h / r²) correlates the minimum width of the swing arm segment 222 with the square of the outer contour dimension of the free segment 223, comprehensively reflecting the matching relationship between the two springs 220 in terms of both stiffness and mass. The minimum width of the swing arm segment 222 represents the stiffness characteristics, while the square of the radius of the free segment 223 is related to the area and mass of the free segment 223. H / R² represents the proportional relationship between the stiffness of the first spring 240 and the mass of its free segment 223, and h / r² represents the corresponding proportional relationship of the second spring 250. The quotient of the two ratios reflects the degree of difference in the stiffness and mass ratio of the two springs 220.

[0042] When (H / R²) / (h / r²) is less than 0.7, the stiffness and mass ratio of the first spring 240 is lower than that of the second spring 250. This means the relative stiffness of the first spring 240 is insufficient, or the mass of its free section 223 is too large. Consequently, the rebound speed of the first spring 240 cannot meet the requirements for rapid closing under high-frequency operating conditions, weakening its effect of reducing the return flow. When (H / R²) / (h / r²) is greater than 2.3, the difference in stiffness and mass ratio between the two springs 220 is too large. The relative stiffness of the first spring 240 is too high, or the relative stiffness of the second spring 250 is too low. Under low-frequency operating conditions, the opening resistance of the first spring 240 is too high, and the rebound speed of the second spring 250 is too slow under high-frequency operating conditions, resulting in an excessively large return flow. This leads to a decrease in overall performance.

[0043] By controlling (H / R²) / (h / r²) within the range of 0.7 to 2.3, a reasonable matching relationship is maintained between the stiffness of the two springs 220 and the mass of their respective free sections 223. Under high-frequency operating conditions, the first spring 240 has sufficient rebound speed to control the reflux flow rate, and the absolute intake volume of the second spring 250 increases, but the reflux flow rate is controlled within an acceptable range. Under low-frequency operating conditions, the opening resistance of both springs 220 is at a reasonable level, and the power consumption of the compressor will not increase due to the excessive stiffness of one spring 220.

[0044] Reference Figure 2 and Figure 3 As shown, in the embodiment of the present invention, the radius R of the first arc segment 241 and the radius r of the second arc segment 251 satisfy: R ≥ r. It can be understood that the first arc segment 241 and the second arc segment 251 respectively determine the effective area of ​​the free segments 223 of the first and second springs 240 and 250 when they cover the intake port 110. When R is less than r, the stiffness of the first spring 240 will decrease, resulting in a slower rebound speed, increased return flow during high-frequency operation, reduced effective intake volume, and impact on compressor efficiency.

[0045] Therefore, setting the radius of the first arc segment 241 to be greater than or equal to the radius of the second arc segment 251 ensures the responsiveness of the spring 220 during high-frequency operation and reduces backflow. Simultaneously, the larger radius R of the free segment 223, combined with the larger swing arm width H, results in a more structurally harmonious design, reducing stress concentration. The smaller radius r of the free segment 223, combined with the narrower swing arm width h, helps reduce the moment of inertia of the second spring 250, thereby reducing the opening resistance of the spring 220 during low-frequency compressor operation.

[0046] Reference Figure 2 and Figure 3 As shown in the embodiment of the present invention, the minimum width of one swing arm segment 222 is H, and the minimum width of the other swing arm segment 222 is h, satisfying: 1.4 ≤ H / h ≤ 2.4. For example, the value of H / h can be 1.4, 1.5, 1.8, 2, 2.2, 2.4, etc. The ratio H / h reflects the degree of difference in stiffness design between the two springs 220. When H / h is less than 1.4, the difference in swing arm width between the two springs 220 is small, and the stiffness characteristics tend to be consistent, making it difficult to simultaneously achieve high and low frequency performance. When H / h is greater than 2.4, the difference in stiffness between the two springs 220 is too large. At this time, two extreme cases will occur: one is that h is too small, resulting in the second spring 250 having too low stiffness. Although it is easy to open at low frequencies, it rebounds very slowly at high frequencies, the return flow increases dramatically, and fatigue fracture may even occur; the other is that H is too large, resulting in the first spring 240 having too high stiffness, extremely high opening resistance, and even at low frequencies, it is difficult to open fully, resulting in insufficient air intake. Therefore, the solution in this embodiment controls the ratio between 1.4 and 2.4, which can ensure that the two tongue springs 220 maintain a moderate gradient in stiffness, achieve functional complementarity, and take into account the performance requirements of high frequency and low frequency.

[0047] Reference Figure 3 As shown in the embodiment of the present invention, the width of the swing arm segment 222 gradually decreases and then gradually increases along a second direction perpendicular to the first direction. It can be understood that the swing arm segment 222 is the elastic deformation region connecting the fixed segment 221 and the free segment 223, and it bears repeated bending stress during operation. Designing the swing arm segment 222 with its width gradually decreasing and then gradually increasing along the second direction, with the side of the swing arm segment 222 closer to the fixed segment 221 being wider, capable of withstanding a larger bending moment; and the side of the swing arm segment 222 closer to the free segment 223 being narrower, increases the flexibility of the end, which is beneficial for the flexible swinging of the free segment 223. This variable cross-section design makes the stress distribution along the length of the swing arm more uniform, thereby improving its fatigue resistance and service life while ensuring the elastic response of the tongue spring 220.

[0048] Reference Figure 2 and Figure 3As shown, in the embodiment of the present invention, the width of the fixing segment 221 gradually increases along a second direction perpendicular to the first direction. It can be understood that the fixing segment 221 fixes the tongue spring 220 to the body 210. Since the width of the fixing segment 221 gradually increases along the second direction, the cross-section at the connection between the fixing segment 221 and the body 210 is the widest. This design enhances the connection strength at the root, effectively resisting the shear force and bending moment transmitted to the root by the repeated oscillation of the tongue spring 220, preventing root breakage. Simultaneously, the gradually increasing width forms a smooth transition area, avoiding stress concentration caused by abrupt changes in cross-section, further improving the overall structural reliability of the intake valve plate 200, and also helping to increase the rebound speed of the tongue spring 220 and reduce the backflow rate.

[0049] Reference Figure 2 and Figure 3 As shown in the embodiment of the present invention, the side of the fixed segment 221 and the swing arm segment 222 facing the other tongue spring 220 is the inner edge 226, and the side of the fixed segment 221 and the swing arm segment 222 away from the other tongue spring 220 is the outer edge 227. Along the direction from the free segment 223 towards the fixed segment 221, the inner edge 226 includes a first edge segment 2261, a second edge segment 2262, and a third edge segment 2263 connected in sequence, and the outer edge 227 includes a fourth edge segment 2271 and a fifth edge segment 2272 connected in sequence. In a second direction perpendicular to the first direction, the two first edge segments 2261 extend in a direction away from each other, the two second edge segments 2262 extend in a direction close to each other, and the distance between the two third edge segments 2263 remains constant; the two fourth edge segments 2271 extend in a direction close to each other, and the two fifth edge segments extend in a direction away from each other.

[0050] Understandably, the inner edge 226 and the outer edge 227 form the lateral profile of the spring 220, determining the width variation pattern of the spring 220. Extending from the free segment 223 to the fixed segment 221, the first edge segment 2261 of the inner edge 226 moves away from each other, while the fourth edge segment 2271 of the outer edge 227 moves closer to each other. This indicates that the width of the swing arm segment 222 gradually increases in this region, forming a tapered structure that transitions from the narrower end of the swing arm to the wider root, enhancing the bending resistance of the swing arm root. Subsequently, the second edge segment 2262 of the inner edge 226 moves closer to each other, while the fifth edge segment 2272 of the outer edge 227 moves away from each other. This indicates that the width of the fixed segment 221 increases rapidly as it approaches the connection with the body 210, forming a flared shape similar to a trumpet mouth. This further disperses the stress at the root, preventing fracture failure due to abrupt changes in cross-section. The distance between the two third edge segments 2263 remains unchanged, indicating that the gap between the two tongue springs 220 is constant in the root region closest to the body 210, ensuring the accuracy of the installation positioning, and also reserving a stable space for the middle exhaust structure.

[0051] Reference Figure 2 and Figure 3 As shown, in an embodiment of the present invention, the swing arm segment 222 has a first edge segment 2261 and a fourth edge segment 2271, and the fixed segment 221 has a second edge segment 2262, a third edge segment 2263, and a fifth edge segment 2272. It can be understood that the swing arm segment 222 is primarily responsible for elastic deformation, with the first edge segment 2261 and the fourth edge segment 2271 located on the inner and outer sides respectively, jointly defining the width variation of the swing arm segment 222. By controlling the curvature and orientation of the first edge segment 2261 and the fourth edge segment 2271, the stiffness distribution of each section of the swing arm segment 222 can be adjusted, ensuring it has sufficient flexibility to adapt to rapid response at high frequencies and sufficient strength to resist large-amplitude opening at low frequencies. The fixed segment 221 serves as the connection base, while the second edge segment 2262, the third edge segment 2263, and the fifth edge segment 2272 primarily function to enhance root connection, disperse stress, and provide positioning.

[0052] Reference Figure 2 and Figure 3 As shown in the embodiment of the present invention, the first edge segment 2261, the second edge segment 2262, the fourth edge segment 2271, and the fifth edge segment 2272 are each constructed as arc-shaped segments, while the third edge segment 2263 is constructed as a straight edge. It is understood that the arc-shaped segments have a smooth and continuous tangential direction, which can effectively avoid stress concentration at sharp corners and bends. Designing the first edge segment 2261, the second edge segment 2262, the fourth edge segment 2271, and the fifth edge segment 2272 as arc-shaped allows the stress of the tongue spring 220 to be smoothly transmitted and dissipated along the edges when subjected to alternating loads, thus improving the fatigue life of the tongue spring 220. For components like the swing arm segment 222 that undergo frequent deformation, the arc-shaped edge can also improve airflow characteristics and reduce fluid resistance. The third edge segment 2263, as the positioning edge closest to the root of the body 210, is designed as a straight edge, which is beneficial for manufacturing and also simplifies the mold structure.

[0053] 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 S1 and S2, dashed line S1 connects the first edge segment 2261 and the fourth edge segment 2271 at one end toward the free segment 223, and serves as the boundary line between the free segment 223 and the swing arm segment 222. Dashed line S2 connects the fourth edge segment 2271 and the first edge segment 2261 at one end toward the fixed segment 221, and serves as the boundary line between the swing arm segment 222 and the fixed segment 221.

[0054] Reference Figure 2 and Figure 3As shown in the embodiment of the present invention, the valve body 100 is provided with a first exhaust port 120, and the body 210 further includes a filler plate 230 located between two tongue springs 220. The filler plate 230 and the tongue springs 220 are spaced apart and are provided with a second exhaust port 211, which communicates with the first exhaust port 120. The filler plate 230 is located in the gap between the two tongue springs 220, and its shape matches the contour of the two tongue springs 220, making full use of the spatial layout of the body 210. 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.

[0055] 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.

[0056] 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.

[0057] 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.

[0058] Reference Figure 1As 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.

[0059] A compressor according to one embodiment of the present invention includes the suction valve assembly 1000 of the above embodiment. The compressor can be a reciprocating compressor. 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 tongue springs 220 of the valve plate 200 are connected to the notch 214 of the body 210 via a fixed section 221, and the free section 223 of the tongue springs 220 covers the suction port 110 of 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 tongue springs 220 and two suction ports 110, the suction volume is larger than that of a single-port design, improving the compressor's energy efficiency. Because the minimum width of the swing arm section 222 of the two tongue springs 220 is different, the opening resistance of the two tongue springs 220 is different, resulting in situations where the suction port 110 opens and closes sequentially. The reed 220 with a minimum width of H has a faster rebound speed, which reduces the backflow and increases the effective intake volume, thus improving the compressor's energy efficiency during high-frequency operation. However, its opening resistance is relatively larger than that of the reed 220 with a minimum width of h. The reed 220 with a minimum width of h has lower opening resistance, which is beneficial for improving the compressor's efficiency during low-frequency operation, but its rebound speed is slower than that of the reed 220 with a minimum width of H, resulting in a reduced effective intake volume. Therefore, this embodiment uses two reeds 220 with different minimum widths to balance the compressor's operating requirements at both high and low frequencies, thereby increasing the intake volume to a certain extent while reducing the opening resistance of the reed 220.

[0060] Since the compressor adopts all the technical solutions of the suction valve group 1000 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.

[0061] This invention discloses a refrigeration device according to one embodiment, including 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. The compressor's suction valve assembly 1000 is connected by a valve body 100 and a valve plate 200. Two tongue 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 tongue springs 220 covers the suction port 110 of 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 tongue springs 220 and two suction ports 110, the suction volume is larger than that of a single-port design, improving the compressor's energy efficiency. Because the minimum width of the swing arm section 222 of the two tongue springs 220 is different, the opening resistance of the two tongue springs 220 is different, resulting in the sequential opening and closing of the suction port 110. The reed 220 with a minimum width of H has a faster rebound speed, which reduces the backflow and increases the effective intake volume, thus improving the compressor's energy efficiency during high-frequency operation. However, its opening resistance is relatively larger than that of the reed 220 with a minimum width of h. The reed 220 with a minimum width of h has lower opening resistance, which is beneficial for improving the compressor's efficiency during low-frequency operation, but its rebound speed is slower than that of the reed 220 with a minimum width of H, resulting in a reduced effective intake volume. Therefore, this embodiment uses two reeds 220 with different minimum widths to balance the compressor's operating requirements at both high and low frequencies, thereby increasing the intake volume to a certain extent while reducing the opening resistance of the reed 220.

[0062] 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.

[0063] 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. One end of 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, the minimum width of one of the tongue springs in the swing arm section is H, and the minimum width of the other tongue spring in the swing arm section is h, satisfying: H > h.

2. The intake valve assembly according to claim 1, characterized in that: The tongue spring with a minimum width of H in the swing arm segment is a first tongue spring, and at least a portion of the outer edge of the free segment of the first tongue spring is constructed as a first arc segment with a radius of R. The tongue spring with a minimum width of h in the swing arm section is a second tongue spring, and at least a portion of the outer edge of the free section of the second tongue spring is constructed as a second arc segment with a radius of r. It satisfies: 0.7≤(H / R²) / (h / r²)≤2.

3.

3. The intake valve assembly according to claim 2, characterized in that: The radius R of the first arc segment and the radius r of the second arc segment satisfy: R ≥ r.

4. The intake valve assembly according to claim 1, characterized in that: The minimum width of one of the swing arm segments is H, and the minimum width of the other swing arm segment is h, satisfying: 1.4≤H / h≤2.

4.

5. The intake valve assembly according to claim 1, characterized in that: Along a second direction perpendicular to the first direction, the width of the swing arm segment gradually decreases and then gradually increases.

6. The intake valve assembly according to claim 1 or 5, characterized in that: The width of the fixed segment gradually increases along a second direction perpendicular to the first direction.

7. The intake valve assembly according to claim 1, characterized in that: The side of the fixed section and the swing arm section facing the other tongue spring is the inner edge, and the side of the fixed section and the swing arm section away from the other tongue spring is the outer edge; Along the direction from the free segment to the fixed segment, the inner edge includes a first edge segment, a second edge segment, and a third edge segment connected in sequence, and the outer edge includes a fourth edge segment and a fifth edge segment connected in sequence; In a second direction perpendicular to the first direction, the two first edge segments extend in directions away from each other, the two second edge segments extend in directions close to each other, and the distance between the two third edge segments remains unchanged; the two fourth edge segments extend in directions close to each other, and the two fifth edge segments extend in directions away from each other.

8. The intake valve assembly according to claim 7, characterized in that: The swing arm segment has a first edge segment and a fourth edge segment, and the fixed segment has a second edge segment, a third edge segment and a fifth edge segment.

9. The intake valve assembly according to claim 7, characterized in that: The first edge segment, the second edge segment, the fourth edge segment, and the fifth edge segment are each constructed as arc segments, and the third edge segment is constructed as a straight edge.

10. The intake valve assembly according to claim 1, characterized in that: The valve body is provided with a first vent hole, and the main body also includes a filler piece located between the two tongue springs. The filler piece and the tongue springs are spaced apart and are provided with a second vent hole. The second vent hole is connected to the first vent hole.

11. A compressor, characterized in that: Includes the intake valve assembly as described in any one of claims 1 to 10.

12. A refrigeration device, characterized in that: Includes the compressor described in claim 11.

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