Valve group of miniaturized reciprocating compressor and compressor

Abstract

The utility model provides a kind of valve group and compressor of miniaturization reciprocating compressor, it is related to compressor field, to the problem that the temperature of existing small compressor cylinder head is too high, gas flow resistance increases and leads to efficiency reduction, by the offset structure of valve plate on the valve plate subassembly suction hole, enlarge suction valve port flow area, reduce suction resistance, reduce the pressure loss and friction heat in suction process, to reduce suction overheating, from the source to relieve cylinder head overheating problem, allow to adopt smaller size cylinder hole, meet the demand of compressor miniaturization, the valve tongue both sides of suction valve piece are provided with contraction part to form waist, exhaust hole is arranged between two sides waist, adapt to the compact space of miniaturization valve group, suction muffler outlet and cylinder cover keep apart, leave gap, cut off the heat conduction path between cylinder cover and suction muffler, form heat insulation, reduce suction overheating, reduce cylinder head temperature benign cycle, improve miniaturization reciprocating compressor efficiency.

Description

Technical Field

[0001] This utility model relates to the field of compressors, specifically to a valve assembly and compressor of a miniaturized reciprocating compressor. Background Technology

[0002] When compressors are miniaturized, the corresponding components also need to be designed to be compact. For valve plate components, the heat dissipation space around the cylinder head is greatly compressed, making it difficult to dissipate heat effectively and causing heat accumulation, which leads to overheating of the cylinder head. At the same time, the size of the valve plate and cylinder head of the valve plate component is reduced accordingly, making it inconvenient to arrange the intake valve plate. This results in the diameter or cross-sectional area of ​​the intake valve port and exhaust valve port being forced to shrink, which increases the resistance when the gas passes through, making the flow resistance of the valve port too large, resulting in low efficiency of small reciprocating compressors.

[0003] The valve plate assembly of a traditional reciprocating compressor cannot be directly scaled down proportionally for use in a small reciprocating compressor. During compressor operation, heat generation in the cylinder head is positively correlated with displacement, while heat dissipation capacity is related to surface area. When the valve plate assembly and cylinder head are scaled down proportionally, the volume decreases by an order of magnitude of cubic, and the surface area decreases by an order of magnitude of square, leading to a decrease in heat dissipation efficiency. After miniaturization, the refrigerant compression ratio may increase (due to the reduced cylinder diameter and unchanged stroke), and heat generation during compression becomes more concentrated, further amplifying overheating problems. In traditional valve plate assemblies, the valve opening / closing timing is matched to the compressor piston stroke. After proportional scaling down, the valve port flow area decreases, reducing gas flow, while the piston speed remains unchanged, resulting in insufficient intake or delayed exhaust. Poor heat dissipation around the cylinder head leads to overheating. Furthermore, excessive flow resistance at the valve orifice causes the gas temperature to rise due to frictional heat generation during the intake process. These multiple factors combined result in excessively high refrigerant temperatures inside the cylinder bore at the end of the intake phase. When this overheated refrigerant enters the cylinder, it generates even more heat during compression. As the boundary of the compression chamber, the cylinder head absorbs even more heat, exacerbating the overheating problem. This overheating, in turn, causes the valve plate and other components to heat up through heat conduction, further heating the refrigerant gas flowing through the valve orifice. This leads to a decrease in refrigerant gas density. To maintain the same mass flow rate, the gas velocity needs to increase accordingly, further increasing flow resistance. The combined effect of cylinder head overheating and excessive valve orifice flow resistance makes it difficult for the miniaturized reciprocating compressor to meet performance requirements. Utility Model Content

[0004] The purpose of this invention is to address the shortcomings of existing technologies by providing a valve assembly and compressor for a miniaturized reciprocating compressor. Through the offset structure of the intake port on the valve plate assembly, the flow area of ​​the intake valve port is expanded, reducing intake resistance and decreasing pressure loss and frictional heat generation during the intake process. This alleviates intake overheating and addresses the cylinder head overheating problem at its source. The intake muffler outlet and cylinder head are kept separate, leaving a gap, which cuts off the heat conduction path between the cylinder head and the intake muffler, reducing intake temperature, decreasing heat generation in the cylinder head during compression, and improving the efficiency of the miniaturized reciprocating compressor.

[0005] The primary objective of this invention is to provide a valve assembly for a miniaturized reciprocating compressor, employing the following solution:

[0006] include:

[0007] Cylinder head;

[0008] The valve plate assembly includes a valve plate gasket, an intake valve plate, a valve plate, an exhaust valve plate, a limiting plate, and a cylinder head gasket arranged sequentially from the cylinder to the cylinder head. The valve plate has an intake hole that matches the intake valve plate. The axis of the intake hole is vertically inclined relative to the end face of the valve plate so that the two ends of the intake hole are offset. The end of the intake hole near the cylinder is offset towards the cylinder bore. The valve tongue of the intake valve plate has a contraction part on both sides, forming the waist of the intake valve plate. The exhaust hole of the intake valve plate is arranged between the waists of the intake valve plates on both sides to connect with the exhaust hole on the valve plate.

[0009] The intake muffler has an intake muffler outlet. One side of the intake muffler outlet is attached to the cylinder head gasket and connected to the intake hole, while the other side is abutted against the cylinder head by a retaining spring. The intake muffler outlet and the cylinder head remain separate.

[0010] Furthermore, the cylinder head has a thin-walled structure, and the limiting points on the back of the cylinder head that are used to contact the housing are thickened.

[0011] Furthermore, the cylinder head has four limiting points on its back, each of which is thickened; the edge of the cylinder head facing the cylinder head gasket has a sealing groove.

[0012] Furthermore, the cylinder head is provided with an abutment portion that contacts the retaining ring, and a clearance portion is formed between the abutment portion and the edge of the cylinder head so that the cylinder head can avoid the portion of the intake muffler outlet that does not cooperate with the retaining ring.

[0013] Furthermore, the intake muffler outlet is provided with a protrusion that abuts against the retaining spring, and a gap is left between the intake muffler outlet and the cylinder head.

[0014] Furthermore, the limiting plate is provided with a curved groove, so that one end of the limiting plate forms a limiting plate spring, one side of the limiting plate abuts against the exhaust valve plate, and the other side abuts against the cylinder head.

[0015] Furthermore, the side of the limiting plate that contacts the exhaust valve plate extends to both sides at the highest point of the limiting curved surface to increase the contact area between the exhaust valve plate and the limiting plate.

[0016] Furthermore, a transition surface is provided on the inner wall of the air intake hole, and the transition surface adopts an arc transition.

[0017] The second objective of this invention is to provide a compressor that utilizes the valve assembly of a miniaturized reciprocating compressor as described in the first objective.

[0018] Furthermore, it also includes screws, one end of which passes through the cylinder head and valve plate assembly in sequence before fitting into the cylinder seat.

[0019] Compared with the prior art, the advantages and positive effects of this utility model are:

[0020] To address the issues of excessively high temperatures in existing small compressor cylinder heads due to compressed heat dissipation space, leading to severe refrigerant heating and increased gas flow resistance resulting in reduced efficiency, an offset structure for the suction port on the valve plate assembly is employed. This expands the flow area of ​​the suction valve port, reduces suction resistance, and decreases pressure loss and frictional heat generation during the suction process, thereby mitigating suction overheating and alleviating cylinder head overheating at its source. This allows for the use of smaller cylinder bores, meeting the requirements of compressor miniaturization. The suction valve tongue has contraction sections on both sides forming a waist, with the exhaust port positioned between these waists to fit the compact space of the miniaturized valve plate assembly. The suction muffler outlet is kept separate from the cylinder head, leaving a gap to cut off the heat conduction path between the cylinder head and the suction muffler, preventing direct heat transfer from the cylinder head to the suction muffler and mitigating refrigerant gas overheating within the suction muffler. This lowers the suction temperature, reduces heat generation in the cylinder head during compression, creating a virtuous cycle of heat insulation, reduced suction overheating, and lower cylinder head temperature, ultimately improving the efficiency of the miniaturized reciprocating compressor.

[0021] The thin-walled design reduces the amount of cylinder head material used, lowers weight, and increases internal volume without changing external dimensions, improving compressor efficiency and reducing extra heat generated by inefficiency. This alleviates cylinder head overheating at its source. The four thickened limiting points are given priority in bearing force when the cylinder head collides with the housing. Due to the large thickness of the limiting points, they have strong resistance to deformation and wear, preventing the thin-walled structure from being damaged by collision, ensuring the stability of the cylinder head structure, and maintaining the normal heat dissipation channels without being damaged.

[0022] The sealing groove has a larger contact area with the cylinder head gasket than a flat seal, and the concave-convex structure forms a tortuous leakage channel, which prolongs the gas leakage path, resulting in a better sealing effect and avoiding efficiency reduction caused by refrigerant leakage. Compared with sealing ribs, the groove will not cause shear damage to the gasket, reducing the risk of seal failure.

[0023] The clearance section reduces the area of ​​the cylinder head covering the intake muffler outlet, thereby reducing the contact area between the two, cutting off the heat conduction path, reducing the heating of the muffler by the cylinder head, and reducing intake overheating. Attached Figure Description

[0024] The accompanying drawings, which form part of this specification, are used to provide a further understanding of this utility model. The illustrative embodiments of this utility model and their descriptions are used to explain this utility model and do not constitute an improper limitation of this utility model.

[0025] Figure 1 This is a schematic diagram of the valve assembly of a miniaturized reciprocating compressor in one or more embodiments of the present invention.

[0026] Figure 2 This is a schematic diagram of the back of the cylinder head in one or more embodiments of the present invention.

[0027] Figure 3 This is a schematic diagram of the front of the cylinder head in one or more embodiments of the present invention.

[0028] Figure 4 This is a schematic diagram of the sealing groove in one or more embodiments of the present invention.

[0029] Figure 5 This is a schematic diagram of the intake silencer in one or more embodiments of the present invention.

[0030] Figure 6 This is a schematic diagram of the intake muffler and cylinder head assembly in one or more embodiments of the present invention.

[0031] Figure 7 This is a schematic diagram of the structure of the limiting plate in one or more embodiments of the present invention.

[0032] Figure 8 This is a front view of the limiting plate in one or more embodiments of the present invention.

[0033] Figure 9 This is a front view of the valve plate in one or more embodiments of the present invention.

[0034] Figure 10 for Figure 9 A schematic diagram of the cross-section at point AA of the middle valve plate.

[0035] Figure 11 This is a schematic diagram of the intake valve plate in one or more embodiments of the present invention.

[0036] The components are as follows: 1. Valve plate gasket; 2. Intake valve plate; 3. Valve plate; 4. Exhaust valve plate; 5. Limiting plate; 6. Cylinder head gasket; 7. Cylinder head; 8. Cylinder head bolts; 9. Snap ring; 10. Intake muffler; 11. Back limiting point; 12. Snap ring mating part; 13. Sealing groove; 14. Back protrusion of intake muffler outlet; 15. Gap between intake muffler and cylinder head; 16. Extension parts on both sides of the limiting curved surface; 17. Spring irregular groove; 18. Intake hole; 19. Small groove at the tail of the limiting plate mounting groove; 20. Small groove at the head of the limiting plate mounting groove; 21. Intake hole transition surface; 22. Valve tongue of intake valve plate; 23. Exhaust hole of intake valve plate; 24. Waist of intake valve plate. Detailed Implementation

[0037] Example 1

[0038] In a typical embodiment of this utility model, such as Figures 1-11 As shown, a valve assembly for a miniaturized reciprocating compressor is presented.

[0039] This embodiment provides a valve assembly for a miniaturized reciprocating compressor, aiming to solve the problems of low energy efficiency caused by cylinder head overheating and excessive valve port flow resistance in existing miniature reciprocating compressors, as well as difficulties in valve plate assembly arrangement and poor reliability in compact design. Existing miniature compressors suffer from compressed cylinder head heat dissipation space, leading to heat accumulation and severe heat conduction with the intake muffler 10, resulting in intake overheating and further exacerbating cylinder head temperature increases. The compact design of the valve plate assembly reduces the size of the intake and exhaust valve ports, resulting in unreasonable flow channel arrangement, increased gas flow resistance, and reduced efficiency. In traditional designs, the intake valve plate 2 is inconvenient to arrange in small-sized valve plate assemblies, affecting valve port size and the miniaturization process of the compressor.

[0040] In this embodiment, as Figure 1 As shown, the valve group of the miniaturized reciprocating compressor mainly includes a cylinder head 7, a valve plate assembly, and an intake muffler 10. The valve plate assembly includes a valve plate gasket 1, an intake valve plate 2, a valve plate 3, an exhaust valve plate 4, a limiting plate 5, and a cylinder head gasket 6 arranged sequentially from the cylinder to the cylinder head 7. The intake muffler 10 has an intake muffler 10 outlet. One side of the intake muffler 10 outlet is attached to the cylinder head gasket 6 and connected to the intake hole 18, while the other side is abutted against the cylinder head 7 by a retaining spring 9. The intake muffler 10 outlet and the cylinder head 7 remain separate.

[0041] like Figure 2 , Figure 3 and Figure 4 As shown, the cylinder head 7 adopts a 2.5mm thin-walled structure. The limiting points on the back of the cylinder head 7 that are used to contact the housing are thickened. In this embodiment, four limiting points are set on the back, and the limiting points are higher than other positions and are locally thickened.

[0042] The thin-walled design of cylinder head 7 increases its internal volume while maintaining the same external dimensions, thus improving compressor efficiency. The four-point back stop ensures that the cylinder head 7 contacts the upper housing first upon impact, and the thick back stop point 11 is less prone to deformation and wear. The thin-walled design reduces the material usage and weight of cylinder head 7, lowering costs, while simultaneously increasing internal volume and improving efficiency, indirectly reducing heat generation caused by low efficiency. The four-point back stop ensures reliability under the thin-walled design, preventing damage from impacts, ensuring cylinder head structure stability, and maintaining normal heat dissipation and flow path conditions. When the compressor shakes during operation or transportation, the housing contacts the back stop point 11 of cylinder head 7 first, with the stop point bearing the impact force, while the thin-walled body is protected from direct impact.

[0043] like Figure 3 and Figure 4 As shown, the cylinder head 7 has a sealing groove 13 on the edge facing the cylinder head gasket 6. The sealing groove 13 extends the path of gas leakage to the outside compared to a flat seal, resulting in a better sealing effect and preventing efficiency loss due to refrigerant leakage. Compared to sealing ribs, the sealing groove 13 does not cause shear damage to the gasket, reducing the risk of seal failure and preventing compressor overheating caused by leakage. The cylinder head gasket 6 is embedded in the sealing groove 13, forming an annular sealing band. Under gas pressure, the gasket and the sealing groove 13 fit tightly together, blocking the leakage path. The structure of the sealing groove 13 avoids the cutting of the cylinder head gasket 6 by the ribs, extending the service life of the cylinder head gasket 6.

[0044] Among them, such as Figure 1 , Figure 9 and Figure 10 As shown, the valve plate 3 is provided with an intake hole 18 that cooperates with the intake valve plate 2. The axis of the intake hole 18 is vertically inclined relative to the end face of the valve plate 3, so that the two ends of the intake hole 18 are offset and the end closer to the cylinder is offset towards the cylinder bore.

[0045] By employing an offset design, the opening of the intake port 18 on the cylinder side is shifted towards the center of the cylinder bore while the overall size of the valve plate 3 is reduced. This increases the effective flow area of ​​the intake valve port within a limited space. When the cylinder diameter decreases, the diameter of a traditional straight-through intake port 18 may be reduced due to space constraints. However, the offset design in this embodiment allows the opening of the intake port 18 on the cylinder side of the valve plate 3 to be closer to the cylinder bore, ensuring a larger intake valve port size without increasing the external dimensions of the valve plate 3. This directly expands the flow area of ​​the intake valve port, reduces intake resistance, and minimizes pressure loss during the intake process. Simultaneously, it allows for the use of a smaller cylinder bore, driving compressor miniaturization.

[0046] The valve tongue of the intake valve plate 2 is provided with a contraction part on both sides, forming the waist part 24 of the intake valve plate, i.e., a double waist design. The double waists are distributed between the valve tongue part 22 of the intake valve plate and the root part of the valve tongue of the intake valve plate 2. The exhaust hole 23 of the intake valve plate is arranged between the waist parts 24 of the intake valve plate on both sides to connect with the exhaust hole on the valve plate 3.

[0047] like Figure 11 As shown, the double-waist design makes the shape of the intake valve plate 2 more suitable for the space constraints of the miniaturized valve plate assembly. The tapered sections on both sides of the waist reduce the material usage and volume of the valve plate, improving space utilization. The exhaust port is located between the two waists, optimizing the relative position of the exhaust port on the valve plate and valve plate 3, which facilitates the arrangement of the intake port 18 and the exhaust port under a small cylinder diameter, and avoids interference between the two.

[0048] The offset design of the intake port 18 and the double-waisted intake valve plate 2 increase the flow area of ​​the intake valve port by 15%-20%, reduce flow resistance by 10%-15%, reduce pressure loss during the intake process, improve the compressor delivery coefficient by 8%-10%, and increase the coefficient of performance (COP) by 12%-15%. It adapts to the compact space of miniaturized valve plate assemblies, solving the problem of difficult placement of traditional single-waisted designs in small sizes, ensuring normal installation and operation of the intake valve plate 2; by optimizing the position of the exhaust port, the placement difficulty of the intake port 18 and exhaust port on the valve plate 3 is reduced, further reducing flow resistance and improving efficiency.

[0049] like Figure 5 , Figure 6 As shown, the retaining ring 9 is installed in the groove of the cylinder head 7, supporting the intake muffler 10 and creating a certain gap between the outlet of the intake muffler 10 and the cylinder head 7 to prevent direct contact between the two. Simultaneously, the mating area between the cylinder head 7 and the retaining ring 9 may rise upwards and retract inwards, reducing the area covered by the cylinder head 7 over the outlet of the intake muffler 10. This cuts off the heat conduction path between the cylinder head 7 and the intake muffler 10, preventing heat from the cylinder head 7 from being directly transferred to the intake muffler 10, mitigating overheating of the refrigerant gas inside the intake muffler 10, lowering the intake temperature, and reducing heat generation in the cylinder head during compression.

[0050] It should be noted that cylinder head overheating and excessive valve flow resistance are not independent issues. In small reciprocating compressors, the two are closely related, influencing and exacerbating each other, and jointly restricting the compressor's energy efficiency and reliability.

[0051] When the flow resistance at the valve port is too high, the refrigerant flow velocity through the valve port increases, and the pressure loss increases, causing the gas temperature to rise during the suction process due to frictional heat generation. At the end of the suction phase, the refrigerant temperature inside the cylinder bore is excessively high. After the superheated refrigerant enters the cylinder, the compression process generates even more heat, and the cylinder head, as the boundary of the compression chamber, absorbs even more heat. When the flow resistance at the exhaust valve port is too high, the discharge of high-temperature, high-pressure refrigerant gas is obstructed, prolonging its residence time in the cylinder. This increases the contact time between the cylinder head and the high-temperature gas, leading to increased heat transfer. Simultaneously, the exhaust valve plate 4 frequently strikes the limit plate 5 due to the high flow resistance, intensifying mechanical frictional heat generation, which is transferred to the cylinder head through the valve plate 3, further raising the cylinder head temperature.

[0052] An increase in cylinder head temperature will cause the temperature of components such as valve plate 3 and valve discs to rise through heat conduction, thereby heating the refrigerant gas flowing through the valve port. The increased gas temperature leads to a decrease in density; with a constant flow rate, the mass flow rate per unit time decreases, resulting in a reduction in cooling capacity.

[0053] like Figure 5 and Figure 6 As shown, the cylinder head 7 has an abutment portion that contacts the retaining spring 9, serving as the retaining spring mating part 12. A clearance portion is formed between the abutment portion and the edge of the cylinder head 7, allowing the cylinder head 7 to avoid the portion of the intake muffler 10 outlet that does not mate with the retaining spring 9. The intake muffler 10 outlet has a protrusion that abuts the retaining spring 9, such as... Figure 5 The intake muffler outlet shown has a raised section 14 on its back. A gap exists between the intake muffler outlet 10 and the cylinder head 7. Figure 6 As shown, there is a gap of 15 between the intake muffler and the cylinder head. The cylinder head 7 and the intake muffler 10 are left with a gap, and a protrusion is added to the back of the muffler to cut off the heat conduction path, reduce intake overheating, and reduce cylinder head temperature rise from the source.

[0054] The clearance portion reduces the area of ​​the cylinder head 7 covering the intake muffler 10 outlet, decreasing the contact area between them, cutting off the heat conduction path, reducing the heating of the muffler by the cylinder head 7, and lowering intake overheating. Simultaneously, it prevents the cylinder head 7 from obstructing unnecessary areas of the muffler outlet, ensuring smooth intake airflow and reducing flow resistance. The retaining spring 9, installed at the abutment portion, supports the intake muffler 10. The clearance portion maintains a distance between the outer side of the muffler outlet and the cylinder head 7, allowing airflow to directly enter the intake port 18 from the muffler outlet without obstruction by the cylinder head 7, and reducing heat conduction due to the increased distance.

[0055] The protrusion is supported by the retaining ring 9, which forces the muffler outlet to separate from the cylinder head 7, with a gap of 5-10mm. The gap further blocks heat conduction. Compared with direct contact, the heat transfer efficiency is reduced by more than 30%, which significantly reduces intake overheating and thus reduces the heat generated by the cylinder head due to the compression of overheated gas.

[0056] The limiting plate 5 has a curved groove, so that one end of the limiting plate 5 forms a limiting plate 5 spring. One side of the limiting plate 5 abuts against the exhaust valve plate 4, and the other side abuts against the cylinder head 7. Figure 7 and Figure 8 As shown, the curved groove at the head spring of the limiting plate 5 serves as the spring groove 17. The side of the limiting plate 5 that contacts the exhaust valve plate 4 extends to both sides of the limiting curved surface at its highest point to form the extension portion 16 on both sides of the limiting curved surface, so as to increase the contact area between the exhaust valve plate 4 and the limiting plate 5.

[0057] The irregularly shaped hollow design reduces spring stiffness, solving the problem of inconvenient installation due to small spring size and excessive stiffness in miniaturized designs; the curved extension increases the contact area with the exhaust valve plate 4, reducing impact stress. For example... Figure 9 As shown, the valve plate 3 has a small groove 19 at the tail of the limiting plate mounting groove and a small groove 20 at the head of the limiting plate mounting groove on the front side to fit the limiting plate 5.

[0058] Simultaneously, when the exhaust valve plate 4 closes, it strikes the limiting plate 5. The extended portions 16 on both sides of the limiting curved surface increase the contact area by 20%-30%, reducing the impact stress σ=F / A. This prevents the valve plate from fatigue fracture due to stress concentration and maintains its normal sealing performance. The valve plate end strikes the extended portion of the limiting plate 5 at high speed, distributing the force over a larger area and reducing local stress. The original contact area of ​​10mm² increases to 15mm² after extension, reducing stress by 33% and extending the valve plate life. This ensures proper assembly of the limiting plate 5 and reliable valve plate operation, preventing fatigue fracture of the valve plate due to high impact stress, thereby maintaining the efficient and stable operation of the valve plate assembly.

[0059] like Figure 10 As shown, an air intake transition surface 21 is provided on the inner wall of the air intake 18, and the air intake transition surface 21 adopts an arc transition.

[0060] The arc transition makes the gas flow through the intake port 18 smoother, reducing turbulence and eddies, reducing the local drag coefficient by 15%-20%, reducing flow resistance, reducing pressure loss during intake, and reducing intake temperature due to frictional heat generation, thus alleviating cylinder head overheating.

[0061] When the gas enters the intake port 18 from the silencer, the curved surface guides the airflow to turn smoothly, avoiding sudden changes in flow rate and pressure fluctuations caused by right-angle transitions.

[0062] Example 2

[0063] In another typical embodiment of this utility model, such as Figures 1-11 As shown, a compressor is provided that utilizes the valve assembly of a miniaturized reciprocating compressor as in Example 1.

[0064] A compressor, the core of which is to utilize the valve group of a miniaturized reciprocating compressor as in Example 1, also includes a screw, one end of which passes through the cylinder head 7 and the valve plate assembly in sequence and then engages with the cylinder.

[0065] Traditional compressors, if their valve assemblies are directly scaled down, suffer from a sharp drop in energy efficiency due to issues such as imbalanced heat dissipation between surface area and volume, and insufficient component rigidity. However, this embodiment utilizes a miniaturized reciprocating compressor valve assembly. This miniaturized reciprocating compressor valve assembly, through offset suction port 18 and localized functional enhancement, maintains performance without degradation while achieving miniaturization. Through a progressive design approach—from core valve assembly technology to compressor system integration and then to overall machine performance improvement—a balance between miniaturization and high performance is achieved.

[0066] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A valve train for a miniaturized reciprocating compressor, characterized in that, include: Cylinder head; The valve plate assembly includes a valve plate gasket, an intake valve plate, a valve plate, an exhaust valve plate, a limiting plate, and a cylinder head gasket arranged sequentially from the cylinder to the cylinder head. The valve plate has an intake hole that matches the intake valve plate. The axis of the intake hole is vertically inclined relative to the end face of the valve plate so that the two ends of the intake hole are offset. The end of the intake hole near the cylinder is offset towards the cylinder bore. The valve tongue of the intake valve plate has a contraction part on both sides, forming the waist of the intake valve plate. The exhaust hole of the intake valve plate is arranged between the waists of the intake valve plates on both sides to connect with the exhaust hole on the valve plate. The intake muffler has an intake muffler outlet. One side of the intake muffler outlet is attached to the cylinder head gasket and connected to the intake hole, while the other side is abutted against the cylinder head by a retaining spring. The intake muffler outlet and the cylinder head remain separate.

2. The valve train of a miniaturized reciprocating compressor according to claim 1, characterized in that, The cylinder head has a thin-walled structure, and the limiting points on the back of the cylinder head that are used to contact the housing are thickened.

3. The valve train of the compact reciprocating compressor according to claim 2, wherein The cylinder head has four limiting points on its back, and each limiting point is thickened; the edge of the cylinder head facing the cylinder head gasket has a sealing groove.

4. The valve train of the miniaturized reciprocating compressor of claim 1, wherein The cylinder head is provided with an abutment portion that contacts the retaining ring, and a clearance portion is formed between the abutment portion and the edge of the cylinder head so that the cylinder head can avoid the part of the intake muffler outlet that does not cooperate with the retaining ring.

5. The valve train of the compact reciprocating compressor according to claim 4, wherein The intake muffler outlet is provided with a protrusion that abuts against the retaining spring, and a gap is left between the intake muffler outlet and the cylinder head.

6. The valve assembly of the miniaturized reciprocating compressor as described in claim 1, characterized in that, The limiting plate has a curved groove, so that one end of the limiting plate forms a limiting plate spring, one side of the limiting plate abuts against the exhaust valve plate, and the other side abuts against the cylinder head.

7. The valve train of the compact reciprocating compressor according to claim 6, characterized in that, The limiting plate extends to both sides from the highest point of the limiting curved surface on the side that contacts the exhaust valve plate, so as to increase the contact area between the exhaust valve plate and the limiting plate.

8. The valve train of the miniaturized reciprocating compressor of claim 1, wherein The inner wall of the air intake hole is provided with a transition surface, which is an arc transition surface.

9. A compressor characterized by, The valve assembly of the miniaturized reciprocating compressor as described in any one of claims 1-8 is used.

10. The compressor of claim 9, wherein, It also includes screws, one end of which passes through the cylinder head and valve plate assembly in sequence before fitting into the cylinder seat.

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