Valve plate structure and compressor

Abstract

The invention provides a valve plate structure and a compressor. The valve plate structure comprises a valve plate body. An exhaust hole group is formed in the valve plate body, the exhaust hole group at least comprises a first exhaust hole and a second exhaust hole, and the first exhaust hole and the second exhaust hole are communicated through a first exhaust channel in the exhaust direction of the exhaust hole group by taking the longitudinal section of the valve plate body as a projection plane; and / or the valve plate body is also provided with an air suction hole group, the air suction hole group at least comprises a first air suction hole and a second air suction hole, and the first air suction hole and the second air suction hole are communicated through a first air suction channel in the air suction direction of the air suction hole group by taking the longitudinal section of the valve plate body as a projection plane. According to the multi-hole valve plate communicating structure, gas is complementarily adjusted among the valve holes, the pressure and speed distribution difference is reduced, and the first exhaust channel and the first suction channel are communicated, so that the resistance in the exhaust and suction processes is reduced.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and in particular relates to a valve plate structure and a compressor. Background Art

[0002] Reciprocating piston compressors primarily use the reciprocating motion of the piston to draw in and out gas. The valve plate has an intake and exhaust hole, with an intake and exhaust valve disc mounted on either side. When the compressor draws air in, gas passes through the intake hole, pushes open the intake valve disc, and enters the cylinder. When the compressor exhausts air, gas leaves the cylinder, passes through the exhaust hole, and pushes open the exhaust valve disc. If the valve plate only has a single intake and exhaust hole, the space utilization and gas transmission efficiency of the valve plate are low, which is detrimental to gas intake and exhaust, thus affecting the overall performance of the compressor.

[0003] Currently, piston compressors typically use valve plates with multiple intake and exhaust holes, i.e., multi-porous valve plates. Accordingly, the intake and exhaust valve plates have multiple elastic reeds that can be opened and closed. When the apertures of the intake or exhaust holes on the valve plate differ, the speed at which the gas passes through will differ, and the pressure on the valve plate and the impact force on the valve reed will be different. As a result, after the compressor has been operating for a period of time, the valve reeds of uniform material will not experience the same degree of wear. Instead, one valve reed will be relatively severely damaged and may experience stress failure first. Even if the intake or exhaust holes on the valve plate have the same aperture size, due to the limited space layout of the valve plate and the requirements for setting, when there are a large number of valve holes, the valve reeds also need to have different stiffnesses, considering the exhaust efficiency in different frequency bands. This will also cause the opening and closing speeds of each reed to be different, while affecting the flow of gas, and ultimately leading to large differences in the damage to the reeds. Summary of the Invention

[0004] The present invention provides a valve plate structure and a compressor, which can solve the technical problem that when there are a large number of valve holes, the exhaust efficiency in different frequency bands is taken into consideration, and the stiffness of the valve plate tongue reed is different, resulting in large differences in the damage conditions of each tongue reed.

[0005] The present invention provides a valve plate structure, which includes a valve plate body;

[0006] The valve plate body is provided with an exhaust hole group, the exhaust hole group including at least a first exhaust hole and a second exhaust hole. With the longitudinal section of the valve plate body as a projection plane, in the exhaust direction of the exhaust hole group, the first exhaust hole and the second exhaust hole are connected through a first exhaust channel.

[0007] And / or the valve plate body is also provided with an air suction hole group, the air suction hole group includes at least a first air suction hole and a second air suction hole, and with the longitudinal section of the valve plate body as the projection surface, in the air suction direction of the air suction hole group, the first air suction hole and the second air suction hole are connected through a first air suction channel.

[0008] In some embodiments, the first exhaust channel is opened inside the valve plate body, and the first exhaust channel has a first connecting port and a second connecting port, the first connecting port is connected to the side wall of the first exhaust hole, and the second connecting port is connected to the side wall of the second exhaust hole.

[0009] In some embodiments, the cross-section of the first exhaust channel is circular, and along the length direction of the first exhaust channel, a first connecting trajectory line is formed between the center of the first connecting port and the center of the second connecting port. The first connecting trajectory line is an arc line, and in the exhaust direction of the exhaust hole group, the first connecting trajectory line is convex outward.

[0010] In some embodiments, the longitudinal section of the valve plate body is used as the projection surface, the thickness of the valve plate body is L1, and the cross-sectional diameter of the first exhaust channel is The cross-sectional diameter satisfy:

[0011] In some embodiments, taking the longitudinal section of the valve plate body as the projection surface, the first exhaust hole and the second exhaust hole penetrate the valve plate body in the thickness direction, the vertical distance between the central axis of the first exhaust hole and the central axis of the second exhaust hole is L2, and the radius of the first connecting trajectory line is R1, and the radius R1 satisfies: R1 = 0.3~0.4L2.

[0012] In some embodiments, the first air suction channel is opened inside the valve plate body, and the first air suction channel has a third connecting port and a fourth connecting port. The third connecting port is connected to the side wall of the first air suction hole, and the fourth connecting port is connected to the side wall of the second air suction hole.

[0013] In some embodiments, the cross-section of the first air intake channel is circular, and along the length direction of the first air intake channel, a second communication trajectory line is formed between the center of the third communication port and the center of the fourth communication port. The second communication trajectory line is an arc line, and in the air intake direction of the air intake hole group, the second communication trajectory line is convex outward.

[0014] In some embodiments, taking the longitudinal section of the valve plate body as the projection surface, the thickness of the valve plate body is L1, the cross-sectional diameter of the first air intake channel is φ2, and the cross-sectional diameter φ2 satisfies: φ2=0.3~0.6L1.

[0015] In some embodiments, taking the longitudinal section of the valve plate body as the projection surface, the first air intake hole and the second air intake hole penetrate the valve plate body in the thickness direction, the vertical distance between the central axis of the first air intake hole and the central axis of the second air intake hole is L3, and the radius of the second connecting trajectory line is R2, and the radius R2 satisfies: R2 = 0.2~0.25L3.

[0016] In some embodiments, the exhaust hole group also includes a third exhaust hole, and the intake hole group also includes a third intake hole. Taking the end face of the valve plate body as the projection surface, the geometric centers of the first exhaust hole, the second exhaust hole and the third exhaust hole are located on the same arc line, and the second exhaust hole and the third exhaust hole are connected through a second exhaust channel; the geometric centers of the first intake hole, the second intake hole and the third intake hole are located on the same arc line, and the second intake hole and the third intake hole are connected through a second intake channel.

[0017] A compressor includes a valve plate structure, wherein the valve plate structure is the above-mentioned valve plate structure.

[0018] The valve plate structure and compressor provided by the present invention have the following beneficial effects:

[0019] The porous valve plate connection structure of the present invention enables complementary regulation of gas between the valve holes, reducing the difference in pressure and velocity distribution. The connection setting of the first exhaust channel and the first intake channel respectively reduces the resistance in the exhaust and intake processes, and the energy loss in the gas flow process. The connection channel ensures that the valve plates open and close synchronously, optimizes the gas in and out process, and enables the cylinder to inhale and exhaust gas more fully, thereby improving the gas output and working efficiency of the compressor. The connection between the first exhaust channel and the first intake channel balances the pressure between the exhaust hole and the intake hole respectively, making the stress on each exhaust valve plate and the intake valve plate more uniform, avoiding premature damage or failure of the valve plate due to excessive local stress. The valve plates are evenly stressed and opened and closed synchronously, reducing the impact and wear between the valve plates, reducing the risk of fatigue failure, thereby extending the service life of the valve plates and reducing the frequency of repair and replacement of the valve plates. The interconnected arrangement of the first exhaust channel and the first intake channel helps to reduce the differences in pressure and velocity distribution during the exhaust and intake processes, respectively, establishes pressure coupling between the valve holes, and makes pressure changes in the cylinder smoother, reducing the impact of pressure fluctuations on compressor performance. The reduction in pressure fluctuations and the synchronized opening and closing of the valve plates reduce vibration and impact during compressor operation, lower the noise level, and improve the stability and reliability of compressor operation. The interconnectedness of the first exhaust channel and the first intake channel allows gas to complement and regulate each other between the holes during both the exhaust and intake processes, forming a more stable and uniform gas flow state. The optimized gas flow characteristics allow gas to pass through the valve plate more smoothly, increasing the speed and efficiency of gas flow, and further improving the gas transmission efficiency and overall performance of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for the embodiments or the description of the prior art. Obviously, the drawings described below are merely exemplary, and those skilled in the art can, without inventive effort, derive other implementation drawings based on the provided drawings.

[0021] Figure 1 Schematic diagram of the valve plate structure according to an embodiment of the present invention;

[0022] Figure 2 for Figure 1 Cross-sectional view at AA in the middle;

[0023] Figure 3 for Figure 1 Cross-sectional view at the middle BB;

[0024] Figure 4 is a schematic diagram of an exhaust hole group according to an embodiment of the present invention;

[0025] Figure 5 is a schematic diagram of a first exhaust channel according to an embodiment of the present invention;

[0026] Figure 6 A schematic diagram of an air intake hole group according to an embodiment of the present invention;

[0027] Figure 7 Schematic diagram of a first air intake channel according to an embodiment of the present invention.

[0028] Figures: 1-valve plate body; 2-exhaust hole group; 201-first exhaust hole; 202-second exhaust hole; 203-first exhaust channel; 231-first connecting port; 232-second connecting port; 204-first connecting trajectory line; 205-third exhaust hole; 206-second exhaust channel; 3-intake hole group; 301-first intake hole; 302-second intake hole; 303-first intake channel; 331-third connecting port; 332-fourth connecting port; 304-second connecting trajectory line; 305-third intake hole; 306-second intake channel. DETAILED DESCRIPTION

[0029] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0030] In the description of the present invention, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0031] For ease of description, spatially relative terms such as "on," "above," "on the upper surface of," and "upper" may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in a drawing is inverted, a device described as "above" or "on top of" the other devices or features would then be positioned "below" or "beneath" the other devices or features.

[0032] See also Figures 1 to 3 As shown, according to an embodiment of the present invention, a valve plate structure is provided, which includes a valve plate body 1; an exhaust hole group 2 is provided on the valve plate body 1, and the exhaust hole group 2 includes at least a first exhaust hole 201 and a second exhaust hole 202, and with the longitudinal section of the valve plate body 1 as the projection surface, in the exhaust direction of the exhaust hole group 2, the first exhaust hole 201 and the second exhaust hole 202 are connected through a first exhaust channel 203; and / or an intake hole group 3 is also provided on the valve plate body 1, and the intake hole group 3 includes at least a first intake hole 301 and a second intake hole 302, and with the longitudinal section of the valve plate body 1 as the projection surface, in the intake direction of the intake hole group 3, the first intake hole 301 and the second intake hole 302 are connected through a first intake channel 303.

[0033] It is worth noting that in this embodiment, the apertures of the exhaust and intake holes can be either the same or different. However, each exhaust hole is provided with an exhaust valve plate having different stiffnesses. Similarly, the corresponding intake valve plates for the intake holes also have different stiffnesses. Specifically, the exhaust valve plate is mounted on the side of the valve plate facing the cylinder head / exhaust chamber, covering the corresponding exhaust hole; the intake valve plate is mounted on the side of the valve plate facing the crankcase / intake chamber, covering the corresponding intake hole. In this embodiment, either only the first exhaust channel 203 or the first intake channel 303 can be provided, or both the first exhaust channel 203 and the first intake channel 303 can be provided.

[0034] Specifically, when the piston of the compressor moves upward and compresses the air, the pressure in the cylinder continues to rise. When the pressure exceeds the exhaust chamber pressure (overcoming the elasticity and back pressure of the exhaust valve plate), the exhaust valve plate opens, allowing high-pressure gas to flow from the cylinder into the exhaust chamber through the exhaust hole group 2. Due to the connectivity of the first exhaust channel 203, in the exhaust direction, the gas can complement and adjust each other between the first exhaust hole 201 and the second exhaust hole 202, reducing the pressure and velocity distribution differences between the exhaust valve holes, establishing pressure coupling between the valve holes, ensuring that the valve plates open synchronously, and achieving dynamic balance of valve hole pressure. At this time, the pressure in the cylinder rises rapidly and exceeds the suction chamber pressure. The pressure difference presses the suction valve plate tightly back to the valve plate, closing the suction hole group 3, and preventing the gas from flowing back to the suction chamber.

[0035] Specifically, when the piston starts to move downward, the pressure in the cylinder drops rapidly and is lower than the pressure in the exhaust chamber. The high-pressure gas in the exhaust chamber presses the exhaust valve plate back to the valve plate, closing the exhaust hole group 2, and preventing the high-pressure gas from flowing back into the cylinder. At this time, the pressure in the cylinder is lower than the pressure in the intake chamber. The pressure difference overcomes the elasticity and gravity of the valve plate, causing the intake valve plate to open, allowing gas to flow from the intake chamber into the cylinder through the intake hole group 3. Due to the action of the first intake channel 303, the gas can complement and regulate each other between the first intake hole 301 and the second intake hole 302, reducing the pressure and velocity distribution differences between the intake valve holes, establishing pressure coupling between the valve holes, ensuring that the valve plates are opened synchronously, and achieving dynamic balance of valve hole pressure.

[0036] In this embodiment, the first exhaust channel 203 connects the first exhaust hole 201 and the second exhaust hole 202, allowing the gas to complement and regulate each other in the exhaust direction, forming a smoother exhaust path, reducing exhaust resistance and energy loss. The connection helps balance the pressure between the exhaust holes, establishes pressure coupling between the valve holes, avoids excessive pressure in a single exhaust hole, reduces pressure distribution differences, and ensures the synchronous opening and closing of the exhaust valves, thereby improving exhaust efficiency and preventing gas backflow caused by premature or delayed closure of individual valves, thereby improving the exhaust efficiency of the compressor. The first intake channel 303 connects the first intake hole 301 and the second intake hole 302, allowing the gas to complement and regulate each other in the intake direction, reducing the resistance when the gas flows through the intake holes, allowing the gas to enter the cylinder more smoothly, and improving the intake efficiency. The connection channel helps balance the pressure between the intake holes, establishes pressure coupling between the valve holes, avoids insufficient gas intake due to excessively low pressure in a single intake hole, ensures the synchronous opening and closing of the intake valves, improves the intake efficiency, prevents gas backflow caused by premature or delayed closure of individual valves, and improves the intake efficiency of the compressor.

[0037] In this embodiment, in a conventional single-hole valve plate, uneven force on the valve plate tongue spring can easily lead to local overload. However, the interconnected structure of the multi-hole valve plate enables complementary regulation of gas between the various valve holes, reducing differences in pressure and velocity distribution. The interconnected arrangement of the first exhaust channel 203 and the first intake channel 303 respectively reduces resistance during the exhaust and intake processes, as well as energy loss during gas flow. The interconnected channels ensure synchronous opening and closing of the valve plates, optimizing the gas inflow and outflow process and enabling the cylinder to more fully inhale and expel gas, thereby improving the compressor's gas output and operating efficiency. The interconnectedness of the first exhaust channel 203 and the first intake channel 303 balances the pressure between the exhaust and intake holes, respectively, making the force applied to each exhaust and intake valve plate more uniform, avoiding premature damage or failure of the valve plates due to localized excessive force. The valve plates are uniformly stressed and open and close synchronously, reducing impact and wear between the valve plates and the risk of fatigue failure, thereby extending the service life of the valve plates and reducing the frequency of valve plate maintenance and replacement. The interconnected arrangement of the first exhaust channel 203 and the first intake channel 303 helps to reduce the differences in pressure and velocity distribution during the exhaust and intake processes, respectively, establishes pressure coupling between the valve holes, and makes the pressure changes in the cylinder smoother, reducing the impact of pressure fluctuations on the performance of the compressor. The reduction in pressure fluctuations and the synchronous opening and closing of the valve plates reduce vibration and impact during compressor operation, reduce noise levels, and improve the stability and reliability of compressor operation. The interconnectedness of the first exhaust channel 203 and the first intake channel 303 allows the gas to complement and adjust each other between the various holes during the exhaust and intake processes, forming a more stable and uniform gas flow state. The optimized gas flow characteristics allow the gas to pass through the valve plate more smoothly, increasing the speed and efficiency of the gas flow, and further improving the gas transmission efficiency and overall performance of the compressor.

[0038] See also Figures 1 to 5 As shown, the first exhaust channel 203 is opened inside the valve plate body 1, and the first exhaust channel 203 has a first connecting port 231 and a second connecting port 232. The first connecting port 231 is connected to the side wall of the first exhaust hole 201, and the second connecting port 232 is connected to the side wall of the second exhaust hole 202.

[0039] It is worth noting that in this embodiment, the first exhaust channel 203 is preferably opened inside the valve plate body 1. In other embodiments, the first exhaust channel 203 can also be set on the end face of the valve plate body 1 or a connecting structure can be set outside the valve plate body 1. The specific setting of the first exhaust channel 203 can be flexibly adjusted according to the structure of the valve plate and the valve sheet. The setting position of the first exhaust channel 203 needs to ensure that the two exhaust holes can be connected.

[0040] Specifically, when the piston moves upward and begins to exhaust, the pressure in the cylinder rises to a level sufficient to overcome the elasticity of the exhaust valve plate and the back pressure in the exhaust chamber, and the exhaust valve plate opens. High-pressure gas flows from the cylinder to the exhaust hole group 2. Some of the gas flows into the first exhaust channel 203 through the first connecting port 231 on the side wall of the first exhaust hole 201, and then enters the second exhaust hole 202 through the second connecting port 232, where it merges with the gas directly discharged from the second exhaust hole 202 and is discharged into the exhaust chamber. Alternatively, the gas in the second exhaust hole 202 flows into the first exhaust hole 201. The first exhaust channel 203 connects the two exhaust holes, and the gas between the holes is complementary and regulated.

[0041] In this embodiment, the first exhaust channel 203 is opened inside the valve plate body 1, avoiding the need to add additional pipes or other connecting structures outside the valve plate, making the entire valve plate assembly more compact, saving space inside the compressor, and facilitating the overall miniaturization of the compressor. The setting of the internal channel realizes the integration of functions, integrating the functions such as gas guidance and regulation into the valve plate body 1, simplifying the structure of the compressor, and improving the coordination between the various components. In addition, the internal channel can provide a more direct and smoother gas flow path, reducing the bends and turns of the gas during the flow process, thereby reducing the flow resistance, allowing the gas to be discharged from the cylinder to the exhaust chamber more quickly and efficiently. Opening a channel inside the valve plate body 1 can also more accurately control the connection area and path between the exhaust holes, thereby better achieving pressure balance between the exhaust holes, reducing the pressure difference between the exhaust holes, and improving the pressure coupling effect.

[0042] In this embodiment, the first exhaust channel 203 connects the first exhaust hole 201 and the second exhaust hole 202, allowing gas to complement and regulate each other between the two holes, establishing pressure coupling, balancing the pressure between the exhaust holes, reducing differences in pressure and velocity distribution, preventing damage to the valve plate due to excessive pressure in a single hole, and improving exhaust efficiency. The balanced pressure distribution ensures the synchronous opening and closing of the exhaust valve plate, improving exhaust efficiency, avoiding impact and wear caused by premature or delayed closure of individual valve plates, reducing the risk of valve plate deformation and damage, and extending the service life. During the exhaust process, the first exhaust channel 203 forms a communication path with the other exhaust holes and the exhaust chamber. When high-pressure gas flows into the exhaust chamber, the channel dynamically balances the pressures of the exhaust holes, preventing the high-pressure gas from flowing back into the cylinder.

[0043] See also Figures 1 to 5 As shown, the cross-section of the first exhaust channel 203 is circular. Along the length direction of the first exhaust channel 203, a first connecting trajectory line 204 is formed between the center of the first connecting port 231 and the center of the second connecting port 232. The first connecting trajectory line 204 is an arc line, and in the exhaust direction of the exhaust hole group 2, the first connecting trajectory line 204 is convex outward.

[0044] Specifically, as the piston begins to move upward, the gas in the cylinder is compressed, and the pressure gradually increases. When the pressure in the cylinder is sufficient to overcome the elasticity of the exhaust valve plate and the back pressure in the exhaust chamber, the exhaust valve plate opens, allowing the high-pressure gas to exit the cylinder. Some of the gas flows into the first exhaust channel 203 through the first connecting port 231 on the sidewall of the first exhaust hole 201. Due to the circular cross-section of the first exhaust channel 203, the gas flows smoothly and with minimal resistance upon entering the channel. The gas flows along the curved first connecting trajectory 204 within the first exhaust channel 203, and the curved shape gradually changes the direction of the gas flow. The gas flows out of the second connecting port 232 of the first exhaust channel 203 and enters the second exhaust hole 202. Guided by the curved trajectory, the gas enters the second exhaust hole 202 smoothly. The gas entering the second exhaust hole 202 merges with the gas discharged directly from the second exhaust hole 202, and together they flow into the exhaust chamber. At this point, the pressure difference between the exhaust holes is reduced, and the gas flow is more uniform. It is worth noting that, in this embodiment, the flow direction between the first exhaust hole 201 and the second exhaust hole 202 is determined by the aperture size between the first exhaust hole 201 and the second exhaust hole 202 and the stiffness of the exhaust valve plate, and flows from the exhaust hole with high pressure to the exhaust hole with low pressure through the first exhaust channel 203.

[0045] In this embodiment, from a gas dynamics perspective, the curved, outwardly convex first communication trajectory 204 conforms to the gas flow curve. Refrigerant has a low density and, in its gaseous state, tends to float upward. Therefore, the convex structure facilitates refrigerant flow and transfer. When gas flows from the first exhaust port 201 into the first exhaust channel 203, the outwardly convex curve guides the gas in a more streamlined direction, allowing the gas to turn more smoothly and enter the second exhaust port 202. During the exhaust process, high-pressure gas within the cylinder must be discharged through the exhaust port. The outwardly convex curved trajectory ensures a more uniform pressure distribution between the exhaust port and the channel. As the gas flows, the curved shape helps balance the local pressure around the exhaust port, preventing unstable gas flow caused by sudden pressure changes. This arrangement also allows gas to better utilize the space between the exhaust port and the channel during the exhaust process. The curved trajectory allows gas to flow over a larger area, avoiding gas accumulation or poor flow caused by an improper channel shape, thereby ensuring efficient exhaust. In addition, uniform gas flow and pressure distribution can reduce the noise and vibration caused by pressure shock during the exhaust process. The outward-convex arc trajectory makes the gas flow smoother, reducing the impact force of the gas on the exhaust hole and channel wall, thereby reducing the generation of noise and vibration.

[0046] See also Figures 1 to 5 As shown, the longitudinal section of the valve plate body 1 is the projection surface, the thickness of the valve plate body 1 is L1, and the cross-sectional diameter of the first exhaust channel 203 is Cross-sectional diameter satisfy:

[0047] In this embodiment, the cross-sectional diameter In the range of 0.3~0.5L1, it can provide enough flow space for gas, make the flow smoother, reduce flow resistance and energy loss, and the cross-sectional diameter is too small. Will increase flow velocity and resistance, while too large a cross-sectional diameter If the channel cross-sectional area is too large, the gas flow may be dispersed. It helps to optimize the flow velocity distribution in the exhaust channel. During the exhaust process, when the gas flows from the exhaust hole into the connecting channel, the appropriate channel cross section can effectively control the gas flow velocity, making it more evenly distributed, avoiding the adverse effects of excessively high or low flow velocity on the gas flow, and improving the exhaust efficiency. And the appropriate cross-sectional diameter It helps to form a more uniform pressure distribution between the exhaust holes. When the gas flows in the exhaust channel, the appropriate channel cross section can reduce the pressure difference between the exhaust holes, making the pressure between the exhaust holes more balanced, which is conducive to the stable discharge of gas. By controlling the cross-sectional diameter of the exhaust channel, the pressure coupling between the exhaust holes can be enhanced. This pressure coupling makes the gas flow between the exhaust holes affect and complement each other, thereby achieving a more stable pressure balance and improving the exhaust efficiency. In addition, the cross-sectional diameter In the range of 0.3~0.5L1, the structural strength of the valve plate body 1 can be ensured. If the cross-sectional diameter If the cross-sectional diameter is too large, the strength of the valve plate will be weakened, making it easy to deform or damage during high-pressure exhaust. This arrangement ensures the structural integrity and mechanical strength of the valve plate while meeting gas flow requirements. This helps optimize internal space utilization within the valve plate. While ensuring sufficient flow area in the exhaust passage, keeping the passage cross-sectional diameter within a reasonable range prevents the valve plate from becoming excessively large, making the valve plate structure more compact and contributing to the overall miniaturization of the compressor.

[0048] See also Figures 1 to 5 As shown, with the longitudinal section of the valve plate body 1 as the projection surface, the first exhaust hole 201 and the second exhaust hole 202 penetrate the valve plate body 1 in the thickness direction, the vertical distance between the center axis of the first exhaust hole 201 and the center axis of the second exhaust hole 202 is L2, and the radius of the first connecting trajectory line 204 is R1, and the radius R1 satisfies: R1 = 0.3~0.4L2.

[0049] In this embodiment, a suitable radius R1 allows the gas to turn more smoothly when flowing in the first exhaust channel 203, reduces flow resistance, and improves exhaust efficiency. A radius R1 that is too large will cause the gas flow path to bend, resulting in vortices and turbulence; a radius R1 that is too small will cause the gas to turn sharply, increasing resistance. A suitable radius R1 can reduce these phenomena, enhance the dynamic response of pressure between exhaust holes, enable the gas to quickly adjust the flow path, ensure pressure balance, optimize the gas flow distribution between exhaust holes, make the gas output of each exhaust hole more uniform, and make exhaust more efficient.

[0050] See also Figures 1 to 7 As shown, the first air intake channel 303 is opened inside the valve plate body 1, and the first air intake channel 303 has a third connecting port 331 and a fourth connecting port 332. The third connecting port 331 is connected to the side wall of the first air intake hole 301, and the fourth connecting port 332 is connected to the side wall of the second air intake hole 302.

[0051] Specifically, when the piston begins to move downward, the pressure in the cylinder drops rapidly, becoming lower than the pressure in the intake chamber. This creates a pressure differential, overcoming the elasticity and gravity of the intake valve disc, causing the intake valve disc to open. Low-pressure gas flows from the intake chamber to the intake hole group 3. Some of the gas flows into the first intake channel 303 through the third connecting port 331 on the side wall of the first intake hole 301. The gas flows within the first intake channel 303 and then flows out of the fourth connecting port 332 of the first intake channel 303 and enters the second intake hole 302. The gas entering the second intake hole 302 merges with the gas entering directly from the second intake hole 302 and flows into the cylinder together. If the gas pressure in the second intake hole 302 is lower, the gas can also flow from the second intake hole 302 into the first intake channel 303, and then from the first intake channel 303 into the first intake hole 301, ultimately merging and entering the cylinder. This bidirectional flow capability further enhances the pressure balance between the intake holes.

[0052] In this embodiment, the first intake channel 303 provides a low-resistance path for the gas. The gas can flow into the channel from the first intake hole 301 through the third connecting port 331 and then enter the second intake hole 302 through the fourth connecting port 332, or vice versa. This arrangement makes the gas flow smoother, reduces flow resistance, and improves the gas intake efficiency. The channel arrangement can optimize the flow velocity distribution of the gas between the intake holes, making the flow velocity of the gas more uniform when entering the cylinder, and avoiding unstable gas flow caused by uneven flow velocity. The first intake channel 303 connects the first intake hole 301 and the second intake hole 302 to each other. The gas can complement and regulate each other between the two holes, reducing the pressure difference between the intake holes and achieving dynamic pressure balance. This balancing effect helps to improve the stability of the intake process. Through the connection effect of the first intake channel 303, the pressure coupling between the intake holes is enhanced, making the flow of gas between the intake holes more coordinated, and further improving the pressure balance effect. The optimized gas flow path enables the gas to enter the cylinder from the suction chamber more quickly and smoothly, thereby increasing the suction volume and improving the suction efficiency of the compressor. The uniform flow of gas between the suction hole and the channel makes the suction valve plate more evenly stressed, reduces local stress concentration, reduces the risk of valve plate fatigue failure, and extends the service life of the valve plate. The balanced pressure distribution helps to stabilize the opening and closing process of the suction valve plate, avoids the impact and wear caused by premature or delayed closure of individual valve plates, and improves the reliability and stability of the valve plate. In addition, the first suction channel 303 is opened inside the valve plate body 1. The reasonable setting will not significantly weaken the structural strength of the valve plate. The size and position of the channel have been optimized to ensure that the valve plate can still maintain sufficient mechanical strength when subjected to gas pressure. The setting of the internal channel helps to optimize the space utilization inside the valve plate, making the valve plate structure more compact, which is conducive to the overall miniaturization of the compressor.

[0053] See also Figures 1 to 7 As shown, the cross-section of the first air intake channel 303 is circular. Along the length direction of the first air intake channel 303, a second communication trajectory line 304 is formed between the center of the third communication port 331 and the center of the fourth communication port 332. The second communication trajectory line 304 is an arc line, and in the air intake direction of the air intake hole group 3, the second communication trajectory line 304 is convex outward.

[0054] Specifically, the piston begins to move downward, and the pressure in the cylinder drops rapidly. The pressure in the cylinder is lower than the pressure in the intake chamber, forming a pressure differential that overcomes the elasticity and gravity of the intake valve plate, causing the intake valve plate to open. Low-pressure gas flows from the intake chamber to the intake hole group 3, first reaching the first intake hole 301. Part of the gas flows into the first intake channel 303 through the third connecting port 331 on the side wall of the first intake hole 301. The gas flows along the arc-shaped second connecting trajectory line 304 in the first intake channel 303. The arc-shaped setting gradually changes the direction of gas flow, avoiding a sharp turn. The gas flows out from the fourth connecting port 332 of the first intake channel 303 and enters the second intake hole 302. The gas entering the second intake hole 302 merges with the gas entering directly from the second intake hole 302 and flows into the cylinder together. If the gas pressure in the second air intake hole 302 is low, the gas can also flow from the second air intake hole 302 into the first air intake channel 303, and then from the first air intake channel 303 into the first air intake hole 301, and finally merge into the cylinder. This two-way flow capability further enhances the pressure balance between the air intake holes.

[0055] In this embodiment, the arc-shaped and outwardly protruding second connecting trajectory line 304 can conform to the natural curve of gas flow. When the gas flows from the first suction hole 301 into the first suction channel 303, the arc guides the gas to flow in a more streamlined direction, allowing the gas to turn more smoothly and enter the second suction hole 302. Through the combination of the arc-shaped trajectory line and the circular cross-section, the resistance in the gas flow is reduced, allowing the gas to enter the cylinder more smoothly from the suction chamber. The second connecting trajectory line 304 is an arc and protrudes outward in the suction direction. This setting makes the gas flow between the suction hole and the channel more uniform, reduces the pressure difference between the suction holes, achieves dynamic pressure balance, enhances the pressure coupling between the suction holes, makes the gas flow between the suction holes more coordinated, and further improves the pressure balance effect. The optimized gas flow path enables the gas to enter the cylinder from the suction chamber more quickly and smoothly, thereby increasing the suction volume and improving the suction efficiency of the compressor. The uniform flow of gas between the suction hole and the channel makes the suction valve plate more evenly stressed, reduces local stress concentration, reduces the risk of valve plate fatigue failure, and extends the service life of the valve plate. The balanced pressure distribution helps to stabilize the opening and closing process of the suction valve plate, avoids impact and wear caused by premature or delayed closure of individual valve plates, and improves the reliability and stability of the valve plate.

[0056] See also Figures 1 to 7 As shown, taking the longitudinal section of the valve plate body 1 as the projection surface, the thickness of the valve plate body 1 is L1, the cross-sectional diameter of the first air intake channel 303 is φ2, and the cross-sectional diameter φ2 satisfies: φ2 = 0.3-0.6L1.

[0057] In this embodiment, the appropriate cross-sectional diameter It can provide enough flow space for gas, make the flow smoother, reduce flow resistance and energy loss, and the cross-sectional diameter is too small. Will increase flow velocity and resistance, while too large a cross-sectional diameter If the channel cross-sectional area is too large, the gas flow may be dispersed, eddy currents and turbulence may be generated, and the flow resistance may be increased. It helps to optimize the flow velocity distribution in the suction channel. During the suction process, when the gas flows into the channel from the suction hole, the appropriate channel cross section can effectively control the gas flow velocity, making it more evenly distributed, avoiding the adverse effects of excessively high or low flow velocity on the gas flow, and improving the suction efficiency. It helps to form a more uniform pressure distribution between the suction holes. When the gas flows in the suction channel, the appropriate channel cross section can reduce the pressure difference between the suction holes, making the pressure between the suction holes more balanced, which is conducive to the stable inhalation of the gas. By controlling the cross-sectional diameter of the suction channel, the pressure coupling between the suction holes can be enhanced. This pressure coupling makes the gas flow between the suction holes affect and complement each other, thereby achieving a more stable pressure balance and improving the suction efficiency. Cross-sectional diameter It can increase the suction volume of the suction channel. During the suction process, the gas can enter the cylinder through the channel more quickly and smoothly, thereby increasing the suction volume, improving the suction efficiency of the compressor, and improving the overall performance of the compressor. Reducing flow resistance and optimizing flow velocity distribution can reduce energy loss during gas flow, so that the compressor consumes less energy during the suction process, improve energy utilization efficiency, and reduce operating costs.

[0058] See also Figures 1 to 7 As shown, with the longitudinal section of the valve plate body 1 as the projection surface, the first air intake hole 301 and the second air intake hole 302 penetrate the valve plate body 1 in the thickness direction, the vertical distance between the center axis of the first air intake hole 301 and the center axis of the second air intake hole 302 is L3, and the radius of the second connecting trajectory line 304 is R2, and the radius R2 satisfies: R2 = 0.2 ~ 0.25L3.

[0059] In this embodiment, the radius R2 makes the gas turn more smoothly when flowing in the intake channel, reduces the flow resistance, and improves the intake efficiency. A radius R2 that is too small will cause the gas flow path to bend, resulting in vortices and turbulence; a radius R2 that is too large will cause the gas to turn sharply, increasing the resistance. The appropriate radius R2 can reduce these phenomena, enhance the pressure balance between the intake holes, make the gas flow more uniform, and make the intake more stable. The appropriate radius R2 can enhance the dynamic response of the pressure between the intake holes, enable the gas to quickly adjust the flow path, and ensure pressure balance.

[0060] As a specific embodiment, the geometric center of the first connecting port 231 and the second connecting port 232 is on the horizontal axis in the thickness direction of the valve plate. Similarly, the geometric center of the third connecting port 331 and the fourth connecting port 332 is on the horizontal axis in the thickness direction of the valve plate, that is, in the horizontal direction, the cross-sections of the first exhaust channel 203 and the second exhaust channel 206 and the connecting trajectory lines are close to the middle position of the valve plate body 1, and the first exhaust channel 203 and the first intake channel 303 are symmetrically arranged about the corresponding connecting trajectory lines, which is conducive to gas circulation. For example, during the exhaust process, the airflow impact speed is relatively large. It is set in the center position, the airflow flows relatively smoothly, and no unbalanced impact is generated, thereby minimizing the unbalanced torque generated by the gas force in the thickness direction of the valve plate body 1.

[0061] See also Figures 1 to 7 As shown, the exhaust hole group 2 also includes a third exhaust hole 205, and the intake hole group 3 also includes a third intake hole 305. Taking the end face of the valve plate body 1 as the projection surface, the geometric centers of the first exhaust hole 201, the second exhaust hole 202 and the third exhaust hole 205 are located on the same arc line, and the second exhaust hole 202 and the third exhaust hole 205 are connected through the second exhaust channel 206; the geometric centers of the first intake hole 301, the second intake hole 302 and the third intake hole 305 are located on the same arc line, and the second intake hole 302 and the third intake hole 305 are connected through the second intake channel 306.

[0062] Specifically, the valve plate body 1 is provided with a plurality of exhaust holes and intake holes. Adjacent exhaust holes are connected by exhaust channels, and adjacent intake holes are connected by intake channels. The second exhaust channel 206 has the same structure as the first exhaust channel 203 and also has a connecting trajectory. The second intake channel 306 also has a connecting trajectory. Due to the provision of multiple exhaust holes and intake holes in this embodiment, the connecting channels between adjacent holes can guide airflow to holes with lower pressure.

[0063] In this embodiment, the arc layout makes the path of gas entering or exiting the cylinder more uniform, reduces the deviation and unevenness of gas flow, and improves gas flow efficiency. The arc arrangement conforms to the principles of gas dynamics, making the gas flow smoother and reducing flow resistance and energy loss. The arc arrangement makes the valve plate structure symmetrical, which helps to improve the mechanical strength and stability of the valve plate. It rationally utilizes the valve plate space, enables multiple holes to be arranged compactly, reduces the size of the valve plate, and is conducive to the miniaturization of the compressor. The arc layout helps to achieve a more uniform pressure distribution between multiple holes, reduces the situation of local excessive or low pressure, improves the pressure balance effect, and the uniform pressure distribution makes the compressor run more smoothly and reduces the vibration and noise caused by pressure fluctuations. Furthermore, for a valve plate body 1 with three exhaust and intake holes, since gas is mostly exhausted or inhaled through the middle hole, the valve plate corresponding to the middle hole has relatively high rigidity, while the valve plates corresponding to the side holes have low rigidity. For example, by using a material with low rigidity, a smaller thickness, and a narrower waist width, dangerous stress points are located at the valve plates on both sides. To address this situation, this embodiment provides a valve plate structure that can balance the pressure difference between the valve holes without changing the size of the valve holes or the structure of the intake and exhaust valve plates. This reduces the impact speed of the valve plate tongue spring when the compressor is running at high speed, thereby improving the reliability of the valve group. In other embodiments, the location of the intake and exhaust holes can be reasonably adjusted according to specific intake and exhaust requirements.

[0064] As a specific embodiment, the inlets and outlets of the first exhaust channel 203 (first and second communication ports 231 and 232), the second exhaust channel 206, the first intake channel 303 (third and fourth communication ports 331 and 332), and the second intake channel 306 are each provided with a rounded corner with a radius of R3. The size of radius R3 can be flexibly adjusted based on the structural strength of the valve plate body 1 and the aperture size of the channel. The provision of the rounded corners can reduce the impact of burrs on gas circulation and prevent the accumulation of lubricating oil in the channel, which could hinder gas circulation. In addition, due to the lower pressure on the intake side, the rounded corner radius R3 at the channel inlet and outlet edges needs to be appropriately increased.

[0065] A compressor includes a valve plate structure, wherein the valve plate structure is the above-mentioned valve plate structure.

[0066] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0067] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention. The above are merely preferred embodiments of the present invention. It should be noted that those skilled in the art may make various improvements and variations without departing from the technical principles of the present invention, and such improvements and variations shall also be considered within the scope of protection of the present invention.

Claims

1. A valve plate structure, characterized in that: include: Valve plate body (1); The valve plate body (1) is provided with an exhaust hole group (2), the exhaust hole group (2) comprising at least a first exhaust hole (201) and a second exhaust hole (202), and with the longitudinal section of the valve plate body (1) as a projection surface, in the exhaust direction of the exhaust hole group (2), the first exhaust hole (201) and the second exhaust hole (202) are connected via a first exhaust channel (203); And / or the valve plate body (1) is further provided with an air intake hole group (3), the air intake hole group (3) comprising at least a first air intake hole (301) and a second air intake hole (302), with the longitudinal section of the valve plate body (1) as a projection surface, in the air intake direction of the air intake hole group (3), the first air intake hole (301) and the second air intake hole (302) are connected via a first air intake channel (303).

2. The valve plate structure according to claim 1, characterized in that: The first exhaust channel (203) is opened inside the valve plate body (1), and the first exhaust channel (203) has a first connecting port (231) and a second connecting port (232), the first connecting port (231) is connected to the side wall of the first exhaust hole (201), and the second connecting port (232) is connected to the side wall of the second exhaust hole (202).

3. The valve plate structure according to claim 2, characterized in that: The cross section of the first exhaust channel (203) is circular, and along the length direction of the first exhaust channel (203), a first communication trajectory line (204) is formed between the center of the first communication opening (231) and the center of the second communication opening (232), the first communication trajectory line (204) is an arc, and in the exhaust direction of the exhaust hole group (2), the first communication trajectory line (204) is convex outward.

4. The valve plate structure according to claim 3, characterized in that: Taking the longitudinal section of the valve plate body (1) as the projection surface, the thickness of the valve plate body (1) is L1, the cross-sectional diameter of the first exhaust channel (203) is φ1, and the cross-sectional diameter φ1 satisfies: φ1=0.3-0.5L1.

5. The valve plate structure according to claim 3, characterized in that: Taking the longitudinal section of the valve plate body (1) as the projection surface, the first exhaust hole (201) and the second exhaust hole (202) penetrate the valve plate body (1) in the thickness direction, the vertical distance between the central axis of the first exhaust hole (201) and the central axis of the second exhaust hole (202) is L2, the radius of the first connecting trajectory line (204) is R1, and the radius R1 satisfies: R1 = 0.3 ~ 0.4L2.

6. The valve plate structure according to claim 1, characterized in that: The first air intake channel (303) is opened inside the valve plate body (1), and the first air intake channel (303) has a third connecting port (331) and a fourth connecting port (332), the third connecting port (331) is connected to the side wall of the first air intake hole (301), and the fourth connecting port (332) is connected to the side wall of the second air intake hole (302).

7. The valve plate structure according to claim 6, characterized in that: The cross section of the first air intake channel (303) is circular, and along the length direction of the first air intake channel (303), a second communication trajectory line (304) is formed between the center of the third communication port (331) and the center of the fourth communication port (332), the second communication trajectory line (304) is an arc, and in the air intake direction of the air intake hole group (3), the second communication trajectory line (304) is convex outward.

8. The valve plate structure according to claim 7, characterized in that: Taking the longitudinal section of the valve plate body (1) as the projection surface, the thickness of the valve plate body (1) is L1, the cross-sectional diameter of the first air intake channel (303) is φ2, and the cross-sectional diameter φ2 satisfies: φ2=0.3-0.6L1.

9. The valve plate structure according to claim 7, characterized in that: Taking the longitudinal section of the valve plate body (1) as the projection surface, the first air intake hole (301) and the second air intake hole (302) penetrate the valve plate body (1) in the thickness direction, the vertical distance between the central axis of the first air intake hole (301) and the central axis of the second air intake hole (302) is L3, the radius of the second connecting trajectory line (304) is R2, and the radius R2 satisfies: R2 = 0.2 ~ 0.25L3.

10. The valve plate structure according to any one of claims 1 to 9, characterized in that: The exhaust hole group (2) further includes a third exhaust hole (205), and the intake hole group (3) further includes a third intake hole (305). Taking the end surface of the valve plate body (1) as a projection surface, the geometric centers of the first exhaust hole (201), the second exhaust hole (202) and the third exhaust hole (205) are located on the same arc line, and the second exhaust hole (202) and the third exhaust hole (205) are connected via a second exhaust channel (206); the geometric centers of the first intake hole (301), the second intake hole (302) and the third intake hole (305) are located on the same arc line, and the second intake hole (302) and the third intake hole (305) are connected via a second intake channel (306).

11. A compressor comprising a valve plate structure, characterized in that: The valve plate structure is the valve plate structure according to any one of claims 1 to 10.

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