Pump body assembly and compressor

Abstract

The invention provides a pump body assembly and a compressor. The pump body assembly comprises an air cylinder, a piston, an air suction piece and a valve plate. A compression cavity is formed in the air cylinder, and the piston reciprocates in the compression cavity; the air suction sheet is installed between the air cylinder and the valve plate, covers the compression cavity, is provided with an air suction valve sheet, and is provided with a first vent groove around the outer contour of the air suction valve sheet; a valve seat exhaust hole and a second vent groove are formed in the valve plate, a first exhaust hole is formed in the air suction piece, and the valve seat exhaust hole and the first exhaust hole are coaxially formed; with the piston end face as a projection plane, one end of the second vent groove communicates with the valve seat exhaust hole, and the projection contour line of the other end of the second vent groove intersects with the projection contour line of the first vent groove. The second vent groove is communicated with the first vent groove, so that the effective flow area is increased, and gas is discharged more smoothly.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of compressors, and particularly relates to a pump body assembly and a compressor. BACKGROUND

[0002] During the operation of the piston compressor, the piston moves linearly in the cylinder, the general exhaust direction of the high-pressure gas in the cylinder is consistent with the movement direction of the piston, is perpendicular to the end face of the piston and points to the exhaust port of the valve seat, at this time, the minimum exhaust flow area is the cross-sectional area of the exhaust port of the valve seat; during the process that the piston continues to move to the position close to the top dead center, the linear distance between the piston and the exhaust port is reduced to the order of tens of microns, at this time, the general exhaust direction of the high-pressure gas in the cylinder is perpendicular to the movement direction of the piston and is parallel to the end face of the piston and points to the exhaust port of the valve seat from the wall surface of the cylinder, at this time, the minimum flow area becomes the product of the linear distance between the piston and the exhaust port of the valve seat and the circumference of the exhaust port of the valve seat, which is much smaller than the cross-sectional area of the exhaust port of the valve seat, with the decrease of the linear distance between the piston and the exhaust port of the valve seat, the minimum exhaust flow area becomes smaller and smaller, the exhaust resistance of the high-pressure gas in the cylinder becomes greater and greater, the gas pressure becomes higher and higher, and over-compression occurs, especially at high frequency, the time required for discharging the high-pressure gas in the cylinder per unit volume is reduced, the exhaust resistance is further increased, the high pressure in the cylinder is higher, and the over-compression condition is more serious, resulting in the increase of the power consumption of the compressor and the decrease of the cooling capacity, and the high-frequency energy efficiency has no advantage. The suction blade of the piston compressor is usually a thin plate punched part, which is punched into the shape of a valve piece through a punching die, and after punching, a suction valve piece cavity groove is formed, which surrounds the entire suction valve piece and is in communication with the inner cavity of the cylinder, when the piston moves to the position close to the top dead center, the exhaust resistance of the high-pressure gas in the compression cavity and the suction valve piece cavity groove is large, and the power consumption is high. SUMMARY

[0003] The application provides a pump body assembly and a compressor, which can solve the technical problem that the exhaust resistance of the high-pressure gas in the compression cavity and the suction valve piece cavity groove is large and the power consumption is high when the piston moves to the position close to the top dead center.

[0004] The application provides a pump body assembly, which comprises a cylinder, a piston, a suction blade and a valve plate.

[0005] A compression cavity is formed in the cylinder, and the piston reciprocates in the compression cavity; the suction blade is installed between the cylinder and the valve plate, the suction blade covers the compression cavity, a suction valve piece is arranged on the suction blade, and a first air passage groove is formed around the outer contour of the suction valve piece.

[0006] The valve plate is provided with a valve seat exhaust hole and a second air passage groove, the suction blade is provided with a first exhaust hole, and the valve seat exhaust hole and the first exhaust hole are coaxially arranged; taking the piston end face as a projection plane, one end of the second air passage groove is communicated with the valve seat exhaust hole, and the projection contour line of the other end of the second air passage groove intersects with the projection contour line of the first air passage groove.

[0007] In some embodiments, taking the piston end face as a projection plane, the projection contour line of the first air passage groove intersects with the outer circle contour line of the piston, or the projection contour line of the first air passage groove is located in the outer circle contour line of the piston.

[0008] In some embodiments, taking the piston end face as a projection plane, the first air passage groove has a head projection contour line and a tail projection contour line, and the head projection contour line and the tail projection contour line respectively intersect with the outer circle contour line of the piston; the projection contour line of the second air passage groove intersects with the projection contour line of the first air passage groove at any position, so that the gas near the inner wall of the compression chamber flows into the first air passage groove, the second air passage groove and the valve seat exhaust hole in sequence.

[0009] In some embodiments, taking the piston end face as a projection plane, the first exhaust hole is arranged eccentrically relative to the center of the piston end face, and the first air passage groove further includes a middle projection contour line, and the projection contour line of the second air passage groove intersects with the middle projection contour line.

[0010] In some embodiments, two second air passage grooves are arranged on the valve plate, and the two second air passage grooves are arranged in a V shape; taking the piston end face as a projection plane, the projection contour lines of the two second air passage grooves respectively intersect with the middle projection contour lines on both sides.

[0011] In some embodiments, the second air passage groove is a circular counterbore groove, and taking the piston end face as a projection plane, the projection contour line of the second air passage groove has a plurality of intersection points with the projection contour line of the first air passage groove.

[0012] In some embodiments, the first exhaust hole is arranged eccentrically relative to the center of the piston end face, the first air passage groove further includes a middle projection contour line, and the second air passage groove is concentrically arranged with the first exhaust hole; taking the piston end face as a projection plane, the projection contour line of the second air passage groove respectively intersects with the middle projection contour line, the tail projection contour line and the outer circle contour line of the piston.

[0013] In some embodiments, the first venting groove has a tail projected profile line when the projected profile line of the first venting groove is located in the outer circular profile line of the piston, the second venting groove comprises a first straight groove and a second straight groove, one end of the first straight groove is communicated with the valve seat exhaust hole, and the other end of the first straight groove has a projected profile line intersecting with the tail projected profile line; one end of the second straight groove is communicated with the valve seat exhaust hole, and the other end of the second straight groove has a projected profile line intersecting with the outer circular profile line of the piston.

[0014] In some embodiments, the first exhaust hole is eccentrically arranged relative to the center of the piston end face, and the suction blade is further provided with a third venting groove and a fourth venting groove, the third venting groove has one end communicated with the middle part of the first venting groove, and the other end of the third venting groove has a projected profile line intersecting with the outer circular profile line of the piston; the fourth venting groove has one end communicated with the head of the first venting groove, and the other end of the fourth venting groove has a projected profile line intersecting with the outer circular profile line of the piston.

[0015] A compressor comprising a pump body assembly, the pump body assembly being the pump body assembly described above.

[0016] The pump body assembly and the compressor provided by the application have the following beneficial effects:

[0017] The second venting groove and the first venting groove of the application are communicated, the effective flow area is increased, the gas is discharged more smoothly, and the gas pressure is too high and the over-compression phenomenon caused by the too small flow area is reduced. By providing an additional exhaust path and increasing the flow area, the high-pressure gas pressure in the cylinder can be reduced, thereby reducing the over-compression phenomenon, the compressor runs faster, and the amount of gas discharged per unit time is larger, the effect of the second venting groove is more significant, the over-compression phenomenon is effectively reduced, and the high-pressure stability of the compressor is maintained. When running at high frequency, the reduction of exhaust resistance and the improvement of exhaust efficiency are particularly important, the second venting groove ensures that the compressor can effectively discharge high-pressure gas when running at high frequency, avoids the accumulation of high-pressure gas and the aggravation of over-compression caused by poor exhaust, and improves the energy efficiency performance of the compressor at high frequency.

[0018] In the present application, by defining the communication relationship between the two ends of the second vent groove and the valve seat exhaust hole and the first vent groove in the projection plane, it is ensured that the gas can flow smoothly from the first vent groove into the second vent groove and then into the valve seat exhaust hole for discharge. This communication is the basis for achieving smooth gas discharge, avoiding the problem of poor gas flow or blockage caused by unreasonable structure. In the exhaust process of the piston compressor, the gas needs to be continuously discharged from the compression chamber. This definition ensures that the flow path of the gas during discharge is continuous without interruption or obstruction, allowing the gas to be discharged stably, reducing the disturbance and pressure fluctuation of the gas during discharge, and improving the stability and reliability of the compressor operation. Defining the communication relationship between the second vent groove and the first vent groove and the valve seat exhaust hole is equivalent to providing an optimized exhaust passage for high-pressure gas. This passage can make the gas discharge from the cylinder more quickly and smoothly, reducing the number of bends and obstructions the gas passes through during discharge, reducing exhaust resistance, and improving exhaust efficiency. The second vent groove is defined and set, and its communication with the first vent groove is not dependent on the size of the gap between the piston and the valve seat exhaust port. Even when the piston is close to the top dead center, it can still provide an effective exhaust path for the gas, ensuring that the gas can be discharged smoothly and avoiding the problem of poor exhaust caused by changes in piston position. BRIEF DESCRIPTION OF DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or prior art description. Obviously, the drawings in the following description are only exemplary, and those skilled in the art can also obtain other drawings according to the provided drawings without creative labor.

[0020] Figure 1 is a schematic view of the pump body assembly in the prior art;

[0021] Figure 2 is an exploded view of the pump body assembly of the embodiment of the present application;

[0022] Figure 3 is a sectional view of the pump body assembly of the embodiment of the present application;

[0023] Figure 4 is a schematic view of the second vent groove of the embodiment of the present application;

[0024] Figure 5 is a schematic view of the intersection of the projection profile line and the middle projection profile line of the second vent groove of the embodiment of the present application;

[0025] Figure 6 is a schematic view of the valve plate when the projection profile line and the middle projection profile line of the second vent groove of the embodiment of the present application intersect;

[0026] Figure 7 Fig. 4 is a schematic view of the air suction piece when the projection profile line of the second vent groove of the embodiment of the present application intersects with the middle projection profile line;

[0027] Figure 8 Fig. 5 is a schematic view of the valve plate when the projection profile line of the first vent groove of the embodiment of the present application is located in the outer circle profile line of the piston;

[0028] Figure 9 Fig. 6 is a schematic view of the air suction piece when the projection profile line of the first vent groove of the embodiment of the present application is located in the outer circle profile line of the piston;

[0029] Figure 10 Fig. 7 is a schematic view of the air suction piece when the projection profile line of the first vent groove of the embodiment of the present application is located in the outer circle profile line of the piston;

[0030] Figure 11 Fig. 8 is a schematic view when the second vent groove of the embodiment of the present application is a circular counterbore groove;

[0031] Figure 12 Fig. 9 is a schematic view of the valve plate when the second vent groove of the embodiment of the present application is a circular counterbore groove;

[0032] Figure 13 Fig. 10 is a schematic view of the air suction piece when the second vent groove of the embodiment of the present application is a circular counterbore groove.

[0033] Fig. 1 is a cylinder; 101 is a compression chamber; 2 is a piston; 3 is an air suction piece; 301 is a first vent groove; 311 is a head projection profile line; 312 is a tail projection profile line; 313 is a middle projection profile line; 302 is a third vent groove; 303 is a fourth vent groove; 304 is a first exhaust hole; 4 is a valve plate; 401 is a valve seat exhaust hole; 402 is a second vent groove; 421 is a first straight groove; 422 is a second straight groove; 5 is an air suction valve piece. DETAILED DESCRIPTION

[0034] The technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, not all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the present application.

[0035] In the description of the present application, it should be understood that the orientation words such as "front, back, up, down, left, right", "transverse, vertical, perpendicular, horizontal" and "top, bottom" and the like indicated orientation or position relationship are generally based on the orientation or position relationship shown in the drawings, only for the convenience of describing the present application and simplifying the description, without making the opposite statement, these orientation words do not indicate and imply that the indicated device or element must have a particular orientation or be constructed and operated in a particular orientation, therefore it cannot be understood as a limitation on the scope of protection of the present application; the orientation words "inner, outer" refer to the inner and outer of the contour of each component itself.

[0036] For the convenience of description, spatial relative terms such as "over", "above", "upper surface", "upper" and the like can be used herein to describe the spatial positional relationship of one device or feature with other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "over" other devices or structures will be positioned "below" or "under" other devices or structures.

[0037] For the convenience of description, spatial relative terms such as "over", "above", "upper surface", "upper" and the like can be used herein to describe the spatial positional relationship of one device or feature with other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "over" other devices or structures will be positioned "below" or "under" other devices or structures. Figures 2 to 13 As shown, according to the embodiment of the present application, a pump body assembly is provided, which comprises a cylinder 1, a piston 2, an air suction piece 3 and a valve plate 4; the cylinder 1 is provided with a compression cavity 101, and the piston 2 reciprocates in the compression cavity 101; the air suction piece 3 is installed between the cylinder 1 and the valve plate 4, the air suction piece 3 covers the compression cavity 101, the air suction piece 3 is provided with an air suction valve piece 5, and the air suction piece 3 is provided with a first air passage 301 around the outer contour of the air suction valve piece 5; the valve plate 4 is provided with a valve seat exhaust hole 401 and a second air passage 402, and the air suction piece 3 is provided with a first exhaust hole 304, the valve seat exhaust hole 401 and the first exhaust hole 304 are coaxially arranged; taking the end surface of the piston 2 as a projection surface, one end of the second air passage 402 communicates with the valve seat exhaust hole 401, and the projection contour line of the other end of the second air passage 402 intersects with the projection contour line of the first air passage 301.

[0038] Specifically, when the piston 2 compresses the gas, the gas pressure in the cylinder 1 rises, and the gas is compressed from the compression chamber 101, at the same time, the high-pressure gas in the cylinder 1 will flow to the first vent groove 301 on the suction valve plate 5, the first vent groove 301 is arranged around the outer contour of the suction valve plate 5 and is in communication with the compression chamber 101. Since one end of the second vent groove 402 on the valve plate 4 is in communication with the valve seat exhaust hole 401, and the projection contour line of the other end intersects the projection contour line of the first vent groove 301, therefore, in the axial direction, the second vent groove 402 is in communication with the first vent groove 301, and the gas will flow from the first vent groove 301 into the second vent groove 402. The second vent groove 402 is in communication with the valve seat exhaust hole 401, and the gas enters the valve seat exhaust hole 401 from the second vent groove 402, and finally is discharged from the cylinder 1 through the valve seat exhaust hole 401, completing the exhaust process.

[0039] In this embodiment, in combination with the description of the above-mentioned prior art, the advantages of the present application are as follows: Figure 1 When the piston 2 approaches the top dead center, the distance between the piston 2 and the valve seat exhaust port is reduced to the micron level, and the second vent groove 402 provides an additional exhaust path for the high-pressure gas, so that the gas can bypass the small gap between the piston 2 and the valve seat exhaust port and be directly discharged, thereby effectively reducing the exhaust resistance and avoiding the problem of poor exhaust due to too small distance. When the linear distance between the piston 2 and the valve seat exhaust port decreases, the minimum exhaust flow area under the traditional condition will decrease sharply, the second vent groove 402 and the first vent groove 301 are in communication, and the effective flow area is increased, so that the gas is discharged more smoothly, and the phenomenon of high gas pressure and over-compression caused by too small flow area is reduced. By providing an additional exhaust path and increasing the flow area, the high-pressure gas pressure in the cylinder 1 can be reduced, thereby reducing the over-compression phenomenon, and when the compressor is running at high frequency, the running speed of the compressor is faster, and the amount of gas discharged per unit time is larger, the role of the second vent groove 402 is more significant, effectively reducing the over-compression phenomenon and maintaining the high-pressure stability of the compressor. When running at high frequency, the reduction of exhaust resistance and the improvement of exhaust efficiency are particularly important, the second vent groove 402 ensures that the compressor can effectively discharge high-pressure gas when running at high frequency, avoids the accumulation of high-pressure gas and the aggravation of over-compression caused by poor exhaust, and improves the energy efficiency performance of the compressor at high frequency.

[0040] In this embodiment, by defining the communication relationship between the two ends of the second vent groove 402 and the valve seat exhaust hole 401 and the first vent groove 301 on the projection plane, it is ensured that the gas can flow smoothly from the first vent groove 301 into the second vent groove 402 and then into the valve seat exhaust hole 401 for discharge. This communication is the basis for achieving smooth gas discharge and avoids the problem of poor gas flow or blockage caused by unreasonable structure. During the discharge process of the piston 2 compressor, the gas needs to be continuously discharged from the compression chamber 101. This definition ensures that the flow path of the gas during discharge is continuous without interruption or obstruction, allowing the gas to be discharged stably, reducing the disturbance and pressure fluctuation of the gas during discharge, and improving the stability and reliability of the compressor operation. Defining the communication relationship between the second vent groove 402 and the first vent groove 301 and the valve seat exhaust hole 401 is equivalent to providing an optimized exhaust passage for high-pressure gas. This passage allows the gas to be discharged from the cylinder 1 more quickly and smoothly, reducing the number of bends and obstructions the gas passes through during discharge, reducing exhaust resistance, and improving exhaust efficiency. The second vent groove 402 is defined and set, and its communication with the first vent groove 301 is independent of the gap size between the piston 2 and the valve seat exhaust port. Even when the piston 2 approaches the top dead center, it can still provide an effective exhaust path for the gas, ensuring that the gas can be discharged smoothly and avoiding the problem of poor exhaust caused by changes in the position of the piston 2.

[0041] For reference Figures 2 to 10 As shown in the figure, taking the end surface of the piston 2 as the projection plane, the projection profile of the first vent groove 301 intersects the outer circular profile of the piston 2, or the projection profile of the first vent groove 301 is located in the outer circular profile of the piston 2.

[0042] Specifically, when the piston 2 approaches the top dead center position, when the projection profile of the first vent groove 301 intersects the outer circular profile of the piston 2, that is, the first vent groove 301 is in communication with the outer circle of the piston 2, the gas adhering to the inner wall of the compression chamber 101 can flow into the first vent groove 301. The high-pressure gas in the cylinder 1 can not only be discharged through the valve seat exhaust hole 401, but also flow to the second vent groove 402 through the first vent groove 301 and then be discharged through the valve seat exhaust hole 401. When the projection profile of the first vent groove 301 is located in the outer circular profile of the piston 2, the gas will also flow into the first vent groove 301 and flow into the valve seat exhaust port through the second vent groove 402.

[0043] In the embodiment, when the projection profile line of the first vent groove 301 intersects with the outer circle profile line of the piston 2, it means that when the piston 2 moves to a certain position (close to the top dead center), the communication between the first vent groove 301 and the inner wall of the cylinder 1 is formed, which is a prerequisite for the gas to flow from the inner wall of the cylinder 1 into the first vent groove 301, so that the gas can smoothly flow into the first vent groove 301 when the piston 2 approaches the top dead center, avoiding the obstruction of gas flow caused by unreasonable structure, and ensuring the continuity and smoothness of gas exhaust. By limiting the communication between the first vent groove 301 and the outer circle of the piston 2, an additional exhaust path for the gas is provided, which ensures that the gas can be smoothly discharged. With the movement of the piston 2, the size of the communication area between the first vent groove 301 and the outer circle of the piston 2 will dynamically change, and when the piston 2 approaches the top dead center, the communication area may increase, thereby dynamically adjusting the effective flow area of the gas, so that the gas can be discharged from the cylinder 1 more quickly. When the projection profile line of the first vent groove 301 is located in the outer circle profile line of the piston 2, it means that when the piston 2 moves to a position close to the top dead center, the first vent groove 301 and the inner wall of the cylinder 1 always keep communication, which ensures that the gas can continuously flow into the first vent groove 301 during the movement of the piston 2, avoids the interruption of gas flow caused by the change of the position of the piston 2, and provides a reliable exhaust path. No matter where the piston 2 is located, the high-pressure gas in the cylinder 1 can be discharged through the first vent groove 301 and the second vent groove 402, which ensures the continuity and stability of the exhaust process. When the projection profile line of the first vent groove 301 is located in the outer circle profile line of the piston 2, the path of the gas flowing from the inner wall of the cylinder 1 into the first vent groove 301 is shorter, which reduces the resistance and energy loss of the gas flow.

[0044] For reference Figures 2 to 10 As shown in the figure, the end surface of the piston 2 is taken as the projection plane, the first vent groove 301 has a head projection profile line 311 and a tail projection profile line 312, both of which are ring grooves, and the head projection profile line 311 and the tail projection profile line 312 intersect with the outer circle profile line of the piston 2 respectively; the projection profile line of the second vent groove 402 intersects with the projection profile line of any position of the first vent groove 301, so that the gas near the inner wall of the compression chamber 101 flows into the first vent groove 301, the second vent groove 402 and the valve seat exhaust hole 401 in turn.

[0045] Specifically, as the piston 2 rises, the head projection profile line 311 of the first vent groove 301 intersects with the outer circle profile line of the piston 2, which means that a communication path is formed between the inner wall of the compression chamber 101 and the first vent groove 301, and the high-pressure gas in the cylinder 1 can flow into the head region of the first vent groove 301 through this path. Similarly, the tail projection profile line 312 of the first vent groove 301 also intersects with the outer circle profile line of the piston 2, so that the high-pressure gas near the inner wall of the compression chamber 101 can also flow into the tail region of the first vent groove 301. The high-pressure gas in the cylinder 1 flows into the first vent groove 301 along the inner wall of the cylinder 1 under the compression of the piston 2, and because the head and tail projection profile lines 312 intersect with the outer circle profile line of the piston 2, respectively, the gas can flow into the first vent groove 301 from multiple positions of the inner wall of the cylinder 1, forming a multi-path intake. After the gas enters the first vent groove 301, it flows in the groove, and the projection profile line of the second vent groove 402 intersects with the projection profile line of the first vent groove 301 at any position, which ensures that the gas in the first vent groove 301 can smoothly flow into the second vent groove 402. During the flow of the gas in the first vent groove 301, when it encounters the intersection position with the second vent groove 402, part of the gas will turn and flow into the second vent groove 402, forming a new flow path. The gas entering the second vent groove 402 continues to flow and moves towards the valve seat exhaust hole 401, and finally, the gas is discharged from the cylinder 1 through the valve seat exhaust hole 401, completing the exhaust process.

[0046] In this embodiment, the head and tail projection profile lines 312 intersect with the outer circle profile line of the piston 2, respectively, so that the gas can flow into the first vent groove 301 from multiple positions of the inner wall of the cylinder 1, forming a multi-path exhaust, increasing the number of exhaust passages, enabling the high-pressure gas in the cylinder 1 to be discharged more quickly and smoothly, reducing the gas residence time, improving the exhaust efficiency, and extending the exhaust time and improving the exhaust volume during the piston 2 rising process. The multi-path exhaust is equivalent to increasing the flow area of the gas, so that the gas experiences less resistance during the discharge process, reducing the pressure of the high-pressure gas in the cylinder 1, thereby reducing the over-compression phenomenon, reducing the power consumption of the compressor, improving the energy efficiency, and the second vent groove 402 intersects with the first vent groove 301 at any position, so that the gas in the first vent groove 301 can automatically select the optimal path to flow into the second vent groove 402 according to the pressure gradient and flow resistance, optimizing the flow path and reducing the bends and obstacles of the gas flow, further reducing the resistance.

[0047] For reference Figures 2 to 10As shown, the first exhaust hole 304 is arranged eccentrically relative to the center of the end face of the piston 2, and the first vent groove 301 further comprises a middle projection contour line 313, and the projection contour line of the second vent groove 402 intersects the middle projection contour line 313.

[0048] Specifically, when the piston 2 approaches the top dead center, the gas pressure in the cylinder 1 reaches a peak value, at this time, the middle projection contour line 313 of the first vent groove 301 intersects the outer circular contour line of the piston 2, and the high-pressure gas in the cylinder 1 begins to flow into the first vent groove 301, and the high-pressure gas in the cylinder 1 can not only flow into the first vent groove 301 from the head and tail portions, but also from the middle portion, forming a multi-path exhaust. After the gas enters the first vent groove 301, it flows along the path in the groove. Since the projection contour line of the second vent groove 402 intersects the middle projection contour line 313 of the first vent groove 301, when the gas encounters the intersection position during the flow process, part of the gas will be diverted and flow into the second vent groove 402. The gas entering the second vent groove 402 continues to flow and is finally discharged from the cylinder 1 through the valve seat exhaust hole 401, completing the exhaust process.

[0049] In this embodiment, the eccentric arrangement of the first exhaust hole 304 makes the gas flow path more optimal, guides the gas to flow in a specific direction, avoids excessive concentration of gas flow in the central area, reduces the central pressure, makes the gas discharge more uniform, and the intersection of the middle projection contour line 313 of the first vent groove 301 and the outer circular contour line of the piston 2 provides a path for the gas to flow into the first vent groove 301 from the middle portion, so that the gas can flow into the cylinder 1 from multiple positions on the inner wall, forming a multi-path exhaust, increasing the exhaust passage, and improving the exhaust efficiency. The high-pressure gas in the cylinder 1 flows into the first vent groove 301 from the head, middle and tail portions, forming a multi-path exhaust, increasing the number of exhaust passages, making the gas discharge more smooth, and reducing the residence time. The multi-path exhaust is equivalent to increasing the gas flow area, making the gas flow resistance smaller, reducing the high-pressure gas pressure in the cylinder 1, reducing the over-compression phenomenon, reducing the power consumption of the compressor, improving the energy efficiency, and the intersection of the second vent groove 402 and the middle projection contour line 313 of the first vent groove 301 allows the gas to flow in the first vent groove 301 to select the optimal path to flow into the second vent groove 402 according to the pressure and resistance, further reducing the resistance. When operating at high frequency, the compressor needs to discharge more gas in a unit of time. The multi-path exhaust and the optimized flow path can better meet the high-frequency exhaust demand, ensure that the gas is discharged in time, avoid excessive pressure and over-compression in the cylinder 1, ensure high-frequency operation performance and efficiency, improve the exhaust efficiency at high frequency, reduce the increase in power consumption caused by the increase in exhaust resistance, and make the energy efficiency advantage of the compressor in high-frequency operation fully play.

[0050] For reference Figures 2 to 10As shown, two second vent grooves 402 are formed on the valve plate 4, the two second vent grooves 402 are arranged in V shape, the second vent grooves 402 are arc grooves, taking the end face of the piston 2 as the projection plane, the projection contour lines of the two second vent grooves 402 respectively intersect with the middle projection contour lines 313 on both sides.

[0051] Specifically, when the piston 2 approaches the top dead center position, the head and tail projection contour lines 312 of the first vent groove 301 respectively intersect with the outer circle contour line of the piston 2, forming a plurality of communication paths, the high-pressure gas in the cylinder 1 begins to flow from the inner wall of the cylinder 1 into the head and tail regions of the first vent groove 301, the high-pressure gas in the cylinder 1 flows along the inner wall of the cylinder 1 to the first vent groove 301 under the driving of the pressure difference, and enters the first vent groove 301 through the communication paths of the head, middle and tail. The projection contour lines of the two second vent grooves 402 respectively intersect with the middle projection contour lines 313 on both sides of the first vent groove 301, providing a clear flow direction for the gas, when the gas in the first vent groove 301 flows to the position intersecting with the second vent groove 402, part of the gas will turn and flow into the second vent groove 402, the gas entering the second vent groove 402 flows along the V-shaped path in the groove and moves towards the valve seat exhaust hole 401. Finally, the gas is discharged from the cylinder 1 through the valve seat exhaust hole 401, completing the exhaust process.

[0052] In this embodiment, the two second vent grooves 402 arranged in a V shape can better guide the flow of gas, allowing the gas to be more evenly distributed after flowing out of the first vent groove 301 and into the valve seat exhaust hole 401, avoiding the concentration of gas in local areas, reducing exhaust dead angles, and improving exhaust efficiency. The two second vent grooves 402 intersect with the middle projection profile line 313 of the first vent groove 301, increasing the number of paths for gas exhaust, and the high-pressure gas in the cylinder 1 can flow into the second vent groove 402 through multiple paths and be exhausted, making the exhaust more smooth and reducing the residence time of the gas in the cylinder 1. The V-shaped second vent groove 402 can make the gas more evenly exhaust from the cylinder 1, avoiding the problem of local high pressure and uneven exhaust caused by concentrated gas exhaust. This uniform exhaust process can improve the overall efficiency of the compressor and reduce energy loss. Since the V-shaped second vent groove 402 provides more exhaust paths, the exhaust process can start earlier and continue during the movement of the piston 2, extending the exhaust time and improving the exhaust volume. The intersection of the two second vent grooves 402 with the first vent groove 301 is equivalent to increasing the flow area of the gas, making the resistance experienced by the gas during the exhaust process smaller, reducing the high-pressure gas pressure in the cylinder 1, thereby reducing the over-compression phenomenon, reducing the power consumption of the compressor, improving energy efficiency, and optimizing the gas flow path. When the gas flows in the first vent groove 301, it can automatically select the optimal flow path according to the pressure gradient and flow resistance when it encounters the intersection position with the two second vent grooves 402, further optimizing the gas flow path and reducing the exhaust resistance.

[0053] For reference Figures 11 to 13 As shown in FIG. 4, as a second embodiment, the first vent groove 301 intersects with the outer circular profile line of the piston 2, preferably the head projection profile line 311 and the tail projection profile line 312 respectively intersect with the outer circular profile line of the piston 2, and the projection profile line of the first vent groove 301 intersects with the outer circular profile line of the piston 2 with the end face of the piston 2 as the projection plane, and the projection profile line of the second vent groove 402 has multiple intersection points with the projection profile line of the first vent groove 301.

[0054] Specifically, the projection profile line of the second vent groove 402 has multiple intersection points with the projection profile line of the first vent groove 301, forming multiple communication paths. The high-pressure gas in the cylinder 1 begins to flow from the inner wall of the cylinder 1 into the first vent groove 301, and under the driving of the pressure difference, the high-pressure gas in the cylinder 1 flows along the inner wall of the cylinder 1 to the first vent groove 301 and enters the first vent groove 301 through the multiple communication paths. The second vent groove 402 is a circular counterbore groove, and its projection profile line has multiple intersection points with the projection profile line of the first vent groove 301. These intersection points provide multiple paths for the gas to flow into the second vent groove 402. When the gas flowing in the first vent groove 301 encounters the intersection points with the second vent groove 402, part of the gas will turn and flow into the second vent groove 402. Because the second vent groove 402 is a circular counterbore groove, the resistance to gas flow in it is small, and the flow is more smooth. The gas entering the second vent groove 402 flows along a circular path in the groove and moves towards the valve seat exhaust hole 401.

[0055] In this embodiment, the multiple intersection points provide multiple paths for the gas to flow into the second vent groove 402, and the high-pressure gas in the cylinder 1 can flow into the second vent groove 402 from multiple positions at the same time, increasing the number of exhaust passages and making the gas exhaust more smooth, reducing the residence time of the gas in the cylinder 1, improving the exhaust efficiency, and increasing the flow area of the gas, which reduces the resistance to the gas during the exhaust process, thereby reducing the over-compression phenomenon, reducing the power consumption of the compressor, and improving the energy efficiency. The second vent groove 402 is a circular counterbore groove, and its shape helps to optimize the gas flow path, making the gas flow more smooth in the groove, reducing flow resistance and energy loss, further reducing exhaust resistance. By providing multiple path exhaust and increasing the flow area, this arrangement helps to stabilize the gas pressure during the exhaust process, reduces pressure fluctuations caused by changes in exhaust resistance, makes the operation of the compressor more stable, reduces vibration and noise caused by pressure fluctuations, and improves the reliability and service life of the compressor.

[0056] For reference Figures 2 to 10 As shown in the figure, the first exhaust hole 304 is eccentrically arranged relative to the center of the end face of the piston 2. The first vent groove 301 also includes a middle projection profile line 313. The second vent groove 402 is concentrically arranged with the first exhaust hole 304. Taking the end face of the piston 2 as the projection plane, the projection profile line of the second vent groove 402 intersects with the middle projection profile line 313, the tail projection profile line 312, and the outer circular profile line of the piston 2, respectively.

[0057] Specifically, when the piston 2 approaches the top dead center position, the head, middle and tail of the first vent groove 301 project profile lines 312 intersect with the outer circle profile line of the piston 2, forming multiple communication paths. The high-pressure gas in the cylinder 1 begins to flow from the inner wall of the cylinder 1 into the head, middle and tail regions of the first vent groove 301. The high-pressure gas in the cylinder 1 flows along the inner wall of the cylinder 1 to the first vent groove 301 under the driving of the pressure difference, and enters the first vent groove 301 through the multiple communication paths. The second vent groove 402 is concentrically arranged with the first exhaust hole 304, ensuring that the gas flowing from the first vent groove 301 into the second vent groove 402 can directly flow in the direction of the valve seat exhaust hole 401. The projection profile lines of the second vent groove 402 intersect with the middle projection profile line 313 and the tail projection profile line 312 of the first vent groove 301, respectively, providing a clear flow direction for the gas. When the gas in the first vent groove 301 flows to the position intersecting with the second vent groove 402, part of the gas will turn and flow into the second vent groove 402. The gas entering the second vent groove 402 flows in the groove and moves in the direction of the valve seat exhaust hole 401.

[0058] In this embodiment, the head, middle and tail of the first vent groove 301 project profile lines 312 intersect with the outer circle profile line of the piston 2, forming multiple communication paths, and the high-pressure gas in the cylinder 1 can flow into the first vent groove 301 from multiple positions, increasing the number of exhaust passages, making the gas discharge smoother, reducing the residence time, and improving the exhaust efficiency. The second vent groove 402 is concentrically arranged with the first exhaust hole 304, and its projection profile line intersects with the middle and tail projection profile lines 312 of the first vent groove 301, providing a clear flow direction for the gas, so that the gas flowing from the first vent groove 301 into the second vent groove 402 can directly flow in the direction of the valve seat exhaust hole 401, optimizing the exhaust path, reducing the exhaust resistance, reducing the bends and obstructions of the gas flow, and making the gas discharge smoother.

[0059] For reference Figures 2 to 13 As shown in FIG. 4, as a third embodiment, taking the end surface of the piston 2 as the projection plane, when the projection profile line of the first vent groove 301 is located in the outer circle profile line of the piston 2, the first vent groove 301 has a tail projection profile line 312, the second vent groove 402 includes a first straight groove 421 and a second straight groove 422, one end of the first straight groove 421 communicates with the valve seat exhaust hole 401, and the other end of the first straight groove 421 projects a profile line intersecting with the tail projection profile line 312; one end of the second straight groove 422 communicates with the valve seat exhaust hole 401, and the other end of the second straight groove 422 projects a profile line intersecting with the outer circle profile line of the piston 2. The corresponding air inlet piece 3 is provided with an exhaust hole, which can directly guide the gas flow into the second straight groove 422.

[0060] Specifically, one end of the first straight slot 421 is in communication with the valve seat exhaust hole 401, and the projection profile line at the other end intersects the tail projection profile line 312 of the first air passage slot 301. When the gas flows in the first air passage slot 301 to the position intersecting the first straight slot 421, part of the gas will turn and flow into the first straight slot 421. One end of the second straight slot 422 is in communication with the valve seat exhaust hole 401, and the projection profile line at the other end intersects the outer circle profile line of the piston 2. The high-pressure gas near the inner wall of the compression chamber 101 can also directly flow into the second straight slot 422 through the other end of the second straight slot 422. The gas entering the first straight slot 421 and the second straight slot 422 flows in the slot, and finally exhausts the cylinder 1 through the valve seat exhaust hole 401, completing the exhaust process.

[0061] In this embodiment, the first straight slot 421 and the second straight slot 422 provide multiple exhaust paths. The high-pressure gas in the cylinder 1 can not only flow into the first straight slot 421 from the first air passage slot 301 for exhaust, but also directly exhaust through the second straight slot 422, making the exhaust more smooth, improving the exhaust efficiency, and reducing the residence time of the gas in the cylinder 1. One end of the second straight slot 422 is in communication with the valve seat exhaust hole 401, and the projection profile line at the other end intersects the outer circle profile line of the piston 2, so that the high-pressure gas near the inner wall of the compression chamber 101 can directly flow into the second straight slot 422 without passing through the first air passage slot 301, shortening the gas flow path and reducing energy loss. When the gas flows in the first air passage slot 301 to the position intersecting the first straight slot 421, part of the gas turns and flows into the first straight slot 421. This arrangement allows the gas to automatically select the optimal flow path according to the pressure gradient and flow resistance, further optimizing the exhaust process. Multiple-path exhaust is equivalent to increasing the flow area of the gas, making the resistance experienced by the gas during the exhaust process smaller, reducing the high-pressure gas pressure in the cylinder 1, thereby reducing the over-compression phenomenon, reducing the power consumption of the compressor, improving the energy efficiency, and providing a direct exhaust path for the high-pressure gas near the inner wall of the compression chamber 101, reducing the bends and obstructions in the flow process, further reducing the exhaust resistance.

[0062] For reference Figures 2 to 13 As shown in the figure, the first exhaust hole 304 is eccentrically arranged relative to the center of the end face of the piston 2. The suction blade 3 is also provided with a third air passage slot 302 and a fourth air passage slot 303. Taking the end face of the piston 2 as the projection plane, one end of the third air passage slot 302 is in communication with the middle part of the first air passage slot 301, and the projection profile line at the other end of the third air passage slot 302 intersects the outer circle profile line of the piston 2. One end of the fourth air passage slot 303 is in communication with the head of the first air passage slot 301, and the projection profile line at the other end of the fourth air passage slot 303 intersects the outer circle profile line of the piston 2.

[0063] Specifically, the high-pressure gas in the cylinder 1 is driven by the pressure difference, one end of the third air slot 302 is communicated with the middle part of the first air slot 301, and the projection contour line of the other end intersects with the outer circular contour line of the piston 2. The gas near the inner wall of the compression chamber 101 flows into the third air slot 302. When the gas flows in the third air slot 302 to the position communicated with the first air slot 301, part of the gas will turn and flow into the first air slot 301. One end of the fourth air slot 303 is communicated with the head of the first air slot 301, and the projection contour line of the other end intersects with the outer circular contour line of the piston 2. The gas near the inner wall of the compression chamber 101 flows into the fourth air slot 303. When the gas flows in the fourth air slot 303 to the position communicated with the first air slot 301, part of the gas will turn and flow into the first air slot 301. When the gas in the first air slot 301 flows to the position intersected with the first straight slot 421, the gas flows into the first straight slot 421 and is discharged from the valve seat exhaust port.

[0064] In this embodiment, the third air slot 302 and the fourth air slot 303 are respectively communicated with the middle part and the head of the first air slot 301, and at the other end, the projection contour line intersects with the outer circular contour line of the piston 2. This allows the high-pressure gas in the cylinder 1 to flow into these air slots from multiple positions, forming a multi-path exhaust, increasing the number of exhaust passages, making the gas discharge more smooth, reducing the residence time, and improving the exhaust efficiency. The third air slot 302 and the fourth air slot 303 provide additional flow paths for the gas, allowing the gas to choose the flow direction more flexibly, optimizing the exhaust path, and when the gas flows in the first air slot 301, part of the gas can turn and flow into the third air slot 302 or the fourth air slot 303, thereby more efficiently discharging the cylinder 1.

[0065] As a specific implementation, two first straight slots 421 are provided, and the projection contour line 312 of the tail of the first air slot on both sides intersects with the two first straight slots 421 respectively. The third air slot 302 is also provided with two, which respectively guide the middle part of the first air slot 301 and the inner wall of the compression chamber 101.

[0066] A compressor comprising a pump body assembly, the pump body assembly being the pump body assembly described above.

[0067] Those skilled in the art will readily understand that the above advantageous modes can be freely combined and superimposed without conflict.

[0068] The above merely describes the preferred embodiments of the present application, but should not be used to limit the present application, and any modification, equivalent replacement, and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application. The above merely describes the preferred embodiments of the present application, but should not be used to limit the present application, and any modification, equivalent replacement, and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims

1. A pump body assembly, characterized in that, include: Cylinder (1), piston (2), intake plate (3), and valve plate (4); The cylinder (1) has a compression chamber (101) and the piston (2) reciprocates in the compression chamber (101); the suction plate (3) is installed between the cylinder (1) and the valve plate (4), the suction plate (3) covers the compression chamber (101), the suction plate (3) is provided with a suction valve plate (5), and the suction plate (3) has a first ventilation groove (301) around the outer contour of the suction valve plate (5); The valve plate (4) is provided with a valve seat exhaust hole (401) and a second vent groove (402), and the air intake plate (3) is provided with a first exhaust hole (304). The valve seat exhaust hole (401) and the first exhaust hole (304) are coaxially arranged. With the end face of the piston (2) as the projection plane, one end of the second vent groove (402) is connected to the valve seat exhaust hole (401), and the projection outline of the other end of the second vent groove (402) intersects with the projection outline of the first vent groove (301).

2. The pump body assembly according to claim 1, characterized in that, With the end face of the piston (2) as the projection plane, the projection outline of the first vent groove (301) intersects with the outer circle outline of the piston (2), or the projection outline of the first vent groove (301) is located in the outer circle outline of the piston (2).

3. The pump body assembly according to claim 2, characterized in that, With the end face of the piston (2) as the projection plane, the first venting groove (301) has a head projection contour line (311) and a tail projection contour line (312), and the head projection contour line (311) and the tail projection contour line (312) intersect with the outer circle contour line of the piston (2) respectively; the projection contour line of the second venting groove (402) intersects with the projection contour line of the first venting groove (301) at any position, so that the gas near the inner wall of the compression chamber (101) flows into the first venting groove (301), the second venting groove (402) and the valve seat exhaust hole (401) in sequence.

4. The pump body assembly according to claim 3, characterized in that, With the end face of the piston (2) as the projection plane, the first exhaust port (304) is eccentrically positioned relative to the center of the end face of the piston (2). The first venting groove (301) also includes a central projection outline (313). The projection outline of the second venting groove (402) intersects with the central projection outline (313).

5. The pump body assembly according to claim 4, characterized in that, Two second vent grooves (402) are provided on the valve plate (4). The two second vent grooves (402) are arranged in a V shape. With the end face of the piston (2) as the projection surface, the projection outlines of the two second vent grooves (402) intersect with the projection outlines (313) of the middle part on both sides.

6. The pump body assembly according to claim 3, characterized in that, The second vent groove (402) is a circular countersunk groove. With the end face of the piston (2) as the projection surface, the projection outline of the second vent groove (402) and the projection outline of the first vent groove (301) have multiple intersection points.

7. The pump body assembly according to claim 6, characterized in that, The first exhaust port (304) is eccentrically positioned relative to the center of the piston (2) end face. The first vent groove (301) also includes a central projection contour line (313). The second vent groove (402) is concentrically positioned with the first exhaust port (304). With the end face of the piston (2) as the projection surface, the projection contour line of the second vent groove (402) intersects the central projection contour line (313), the tail projection contour line (312), and the outer circle contour line of the piston (2), respectively.

8. The pump body assembly according to claim 2, characterized in that, With the end face of the piston (2) as the projection plane, when the projection outline of the first vent groove (301) is located in the outer circle outline of the piston (2), the first vent groove (301) has a tail projection outline (312), and the second vent groove (402) includes a first straight groove (421) and a second straight groove (422). One end of the first straight groove (421) is connected to the valve seat exhaust hole (401), and the projection outline of the other end of the first straight groove (421) intersects with the tail projection outline (312); one end of the second straight groove (422) is connected to the valve seat exhaust hole (401), and the projection outline of the other end of the second straight groove (422) intersects with the outer circle outline of the piston (2).

9. The pump body assembly according to claim 8, characterized in that, The first exhaust port (304) is eccentrically positioned relative to the center of the piston (2) end face. The intake plate (3) is also provided with a third vent groove (302) and a fourth vent groove (303). With the end face of the piston (2) as the projection plane, one end of the third vent groove (302) is connected to the middle of the first vent groove (301), and the projection outline of the other end of the third vent groove (302) intersects with the outer circle outline of the piston (2). One end of the fourth vent groove (303) is connected to the head of the first vent groove (301), and the projection outline of the other end of the fourth vent groove (303) intersects with the outer circle outline of the piston (2).

10. A compressor, comprising a pump body assembly, characterized in that, The pump assembly is the pump assembly according to any one of claims 1 to 9.

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