Compressor valve group and compressor

Abstract

The utility model provides a kind of compressor valve group and compressor, it is related to compressor field, for the current low problem of small displacement compressor suction efficiency, suction hole is greatly offset to cylinder hole center, utilize the idle space that cylinder hole around is not occupied by exhaust hole, avoid and install space conflict with exhaust hole, cylinder cover, to enlarge suction hole reserved space, suction hole is close to cylinder end flared design, the opening diameter of suction hole close to one end of cylinder is greater than the opening diameter of other end, directly increase opening diameter in the space that offset leaves, to increase total area of suction hole, the area of suction hole is significantly increased after flaring, suction volume per unit time increases, reduce suction resistance, make low-pressure refrigerant more smoothly into cylinder, provide basis for efficient compression.

Description

Technical Field

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

[0002] The cylinder head, exhaust valve spring, limit plate, and exhaust valve plate are important components of the cylinder head assembly in the refrigerator compressor's gas path system. The gas path system mainly consists of the cylinder head assembly, piston, cylinder bore, exhaust muffler chamber, and internal exhaust. This type of gas path system primarily uses the reciprocating motion of the piston to generate a pressure difference, causing the intake and exhaust valve plates to open and close, thereby transforming low-pressure, low-temperature refrigerant gas into high-pressure, high-temperature refrigerant gas, thus achieving the cooling effect. Currently, the demand for high efficiency in reciprocating compressors is increasing, and small-displacement, high-efficiency, and reliable valve assembly designs are beneficial for improving performance and reliability. Traditional valve assembly designs are limited by cylinder diameter and manufacturing processes, making it difficult to improve efficiency.

[0003] Due to current limitations on the diameter of small-displacement cylinders, the size of the intake port is restricted. Furthermore, a certain clearance must be maintained between the intake and exhaust ports to allow space for the cylinder head end face width and the intake muffler outlet width. Considering this clearance, it's generally difficult to increase the intake port size, thus hindering efficiency improvements. To pursue high performance, the thickness or width of the valve plate is typically reduced to decrease its stiffness. However, reliability constraints limit the valve plate thickness; currently, the minimum valve plate thickness for reciprocating compressors is 0.152mm. Therefore, valve plate stiffness is constrained, making it difficult to improve efficiency. Utility Model Content

[0004] The purpose of this utility model is to address the deficiencies of the existing technology by providing a compressor valve group and compressor, wherein the suction port on the cylinder bore side of the valve plate is increased by a large offset to increase the suction port area, effectively increasing the thrust surface of the suction valve plate and improving the suction efficiency.

[0005] The primary objective of this invention is to provide a compressor valve assembly, which employs the following solution: The device includes an intake valve plate, a valve plate, an exhaust valve plate, an exhaust valve spring, and a limiting plate arranged sequentially. The valve plate has an intake hole and an exhaust hole. The intake hole is offset towards the center of the cylinder bore at the end closer to the cylinder than at the other end, and the opening diameter of the intake hole at the end closer to the cylinder is larger than the opening diameter at the other end. The intake valve plate cooperates to block the opening of the intake hole at the end closer to the cylinder. The valve plate has a valve plate groove on the side away from the cylinder. The exhaust valve plate, exhaust valve spring, and limiting plate cooperate with the valve plate groove. The exhaust valve plate cooperates to block the opening of the exhaust hole at the end away from the cylinder. The exhaust valve spring abuts against the limiting plate to receive the thrust applied when the exhaust valve plate opens and undergoes elastic deformation.

[0006] Furthermore, the intake valve plate is inclined relative to the side of the valve plate to avoid the exhaust port.

[0007] Furthermore, the front end of the suction valve plate, which mates with the suction hole, is positioned as the suction valve tongue, and a contraction section is provided between the tail end of the suction valve plate and the suction valve tongue.

[0008] Furthermore, the tail end of the valve plate groove extends into an anti-fooling groove, and the tail ends of the exhaust valve plate and exhaust valve spring are provided with protrusions to insert into the anti-fooling groove and constrain the position of the exhaust valve plate and exhaust valve spring.

[0009] Furthermore, the thickness of the exhaust valve plate is 0.12mm-0.13mm.

[0010] Furthermore, one end of the exhaust valve spring is pressed and constrained between the limiting plate and the exhaust valve plate, while the other end extends towards the exhaust port to form a cantilever structure, which is used to contact the exhaust valve plate.

[0011] Furthermore, one end of the exhaust valve plate is pressed and constrained between the exhaust valve spring and the valve plate, while the other end extends towards the exhaust port to form a cantilever structure, which is used to block the exhaust port.

[0012] Furthermore, an exhaust high-pressure ring is provided outside the opening at the end of the exhaust port away from the cylinder, protruding from the bottom surface of the valve plate groove, and the exhaust high-pressure ring abuts against the exhaust valve plate.

[0013] Furthermore, both the outer and inner circles of the exhaust high-pressure ring at one end are made with arc-shaped transition surfaces, and an end plane is provided between the outer and inner circles.

[0014] The second objective of this invention is to provide a compressor that utilizes the compressor valve assembly as described in the first objective.

[0015] Compared with the prior art, the advantages and positive effects of this utility model are: To address the issue of low intake efficiency in current small-displacement compressors, the intake port is significantly offset towards the center of the cylinder bore. This utilizes the unused space around the cylinder bore that is not occupied by the exhaust port, avoiding conflicts with the installation space of the exhaust port and cylinder head. To accommodate the increased intake port size, the intake port is flared near the cylinder end, with the opening diameter at the cylinder end being larger than that at the other end. By directly increasing the opening diameter within the space freed up by the offset, the total area of ​​the intake port is increased. The significantly increased area after the intake port is flared increases the intake volume per unit time, reduces intake resistance, and allows low-pressure refrigerant to enter the cylinder more smoothly, providing a foundation for efficient compression.

[0016] The intake valve plate is arranged at an angle to avoid physical interference with the exhaust port, ensuring that the valve plate can still be installed normally and block the intake port after the intake port is enlarged. At the same time, it is compatible with existing cylinder head, limit plate and other components. Through the offset and tilt design, the intake port is enlarged without changing the matching relationship with the existing cylinder seat, piston and exhaust system. There is no need to replace other core components, reducing the modification cost.

[0017] The reduced thickness of the exhaust valve plate significantly reduces its rigidity; the exhaust port adopts an arc-shaped valve orifice design, and the width of the high-pressure exhaust ring is reduced, effectively reducing viscosity. At the same time, the valve plate's striking action effectively reduces stress concentration and improves reliability; the exhaust valve plate, exhaust valve spring, and valve plate groove root are all designed with anti-foolproof features to prevent the exhaust valve plate and exhaust valve spring from reversing, while also improving the alignment between the exhaust valve plate head and the exhaust port, thereby enhancing reliability and reducing the reversible effect. Attached Figure Description

[0018] 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.

[0019] Figure 1 This is an exploded view of the cylinder head component including the compressor valve assembly in an embodiment of this utility model.

[0020] Figure 2 This is a structural diagram of the valve plate in an embodiment of the present utility model.

[0021] Figure 3 This is a partial view of the assembly of the intake valve plate and valve plate gasket in an embodiment of this utility model.

[0022] Figure 4 This is a partial assembly diagram of the valve plate, exhaust valve plate, exhaust valve spring, and limiting plate in an embodiment of this utility model.

[0023] Figure 5 This is a cross-sectional view of the assembly of the valve plate, exhaust valve plate, exhaust valve spring, and limiting plate in an embodiment of this utility model.

[0024] Figure 6 This is a cross-sectional view of the valve plate in an embodiment of this utility model.

[0025] Among them, 1. intake muffler; 2. cylinder head; 3. cylinder head gasket; 4. limit plate; 5. exhaust valve spring; 6. exhaust valve plate; 7. valve plate; 8. intake valve plate; 9. valve plate gasket; 10. cylinder seat; 11. intake port. Detailed Implementation

[0026] Example 1 In a typical embodiment of this utility model, such as Figures 1-6 As shown, a compressor valve assembly is presented.

[0027] Small displacement compressors have small cylinder diameters, and the intake port 11 needs to maintain a certain distance from the exhaust port to reserve installation space for the cylinder head and intake muffler 1. In traditional designs, the intake port 11 cannot be enlarged. The small area of ​​the intake port 11 results in insufficient intake volume, insufficient thrust of the intake valve plate 8 and difficulty in opening, which directly limits the compressor's intake and exhaust efficiency and makes it difficult to meet the high efficiency requirements.

[0028] Based on this, this embodiment provides a compressor valve group. To solve the above problems, the area of ​​the suction port 11 is increased by optimizing the spatial layout. The suction port 11 of the valve plate 7 adopts an offset combined with a flared structure. The end near the cylinder is offset towards the center of the cylinder bore and avoids the exhaust port area. The opening diameter of this end is larger than that of the end away from the cylinder, so that the suction port 11 is flared in a trumpet shape.

[0029] Specifically, such as Figure 1 As shown, the compressor valve assembly includes a suction valve plate 8, a valve plate 7, an exhaust valve plate 6, an exhaust valve spring 5, and a limiting plate 4 arranged sequentially. The valve plate 7 is provided with a suction hole 11 and an exhaust hole. The suction hole 11 is offset towards the center of the cylinder bore at the end near the cylinder compared to the other end, and the opening diameter of the suction hole 11 at the end near the cylinder is larger than the opening diameter at the other end. The suction valve plate 8 cooperates to block the opening of the suction hole 11 at the end near the cylinder. The valve plate 7 is provided with a groove on the side away from the cylinder. The exhaust valve plate 6, the exhaust valve spring 5, and the limiting plate 4 cooperate with the groove of the valve plate 7. The exhaust valve plate 6 cooperates to block the opening of the exhaust hole at the end away from the cylinder. The exhaust valve spring 5 abuts against the limiting plate 4 to receive the thrust applied when the exhaust valve plate 6 is opened and generate elastic deformation.

[0030] The compressor's suction efficiency depends on the flow area of ​​the suction port 11. The larger the area, the more low-pressure refrigerant gas is drawn in per unit time, providing sufficient working fluid for subsequent compression and refrigeration, directly improving efficiency. The suction port 11 is offset towards the center of the cylinder bore, utilizing the unused space around the cylinder bore that is not occupied by the exhaust port, avoiding conflicts with the installation space of the exhaust port and cylinder head. To reserve space for enlarging the suction port 11, the suction port 11 is designed with an flared opening near the cylinder end, directly increasing the opening diameter within the space freed up by the offset, thereby increasing the total area of ​​the suction port 11, improving suction efficiency, and thus improving the working efficiency of the small compressor.

[0031] On the one hand, increasing the area of ​​the intake port 11 increases the thrust when the valve plate opens, making the valve plate easier to open and improving performance. On the other hand, the distance from the intake port 11 on the cylinder head side of the valve plate 7 to the exhaust port must be greater than a certain distance to ensure sufficient distance for sealing when the cylinder head presses the valve plate 7 with the cylinder head gasket, preventing high-pressure gas from leaking from the cylinder head to the low-pressure side. At the same time, this design ensures compatibility with large-displacement cylinder heads, cylinder head gaskets, and intake mufflers 1, achieving parts standardization.

[0032] The intake valve plate 8 is angled relative to the side of the valve plate 7 to avoid the exhaust port, thus avoiding the space occupied by the exhaust port. The intake valve plate 8 corresponds to and blocks the flared end of the intake port 11 near the cylinder to ensure a seal; other parts of the valve plate 7, such as the exhaust port and groove, maintain compatibility with existing components. The inclined arrangement of the intake valve plate 8 avoids physical interference with the exhaust port, ensuring that the valve plate can still be installed normally and block the intake port 11 after the intake port 11 is enlarged, while also being compatible with existing cylinder head, limit plate 4, and other components.

[0033] The front end of the intake valve plate 8 is positioned to match the intake port 11 as the intake valve tongue. A contraction section is provided between the tail end of the intake valve plate 8 and the intake valve tongue. The contraction section between the tail end and the intake valve tongue enables the intake valve tongue to achieve a smooth transition, narrow waist and low rigidity. The inclined design avoids the exhaust port, ensuring that the intake port 11 does not interfere with the exhaust system after it is flared. The contraction section reduces the material in the waist of the valve plate, reducing the thrust required for opening.

[0034] During intake, the low-pressure gas pushes the intake valve tongue, and the contraction section makes the valve plate easier to deform and open, reducing opening resistance; at the same time, the inclined layout avoids competing for space with the exhaust valve plate.

[0035] The valve plate 7 has a misalignment groove extending from its recessed end. The exhaust valve plate 6 and exhaust valve spring 5 have protrusions at their tail ends to insert into the misalignment groove, thus constraining their position. The misalignment groove extending from the rear of the valve plate 7 extends upwards by 2mm; the protrusions at the tail ends of the exhaust valve plate 6 and exhaust valve spring 5 are fitted into the misalignment groove during assembly. This prevents the exhaust valve plate 6 and exhaust valve spring 5 from being installed backwards, tilted, or misaligned.

[0036] The protrusion can only be inserted along the anti-fooling groove, ensuring that the exhaust valve plate 6 accurately covers the exhaust hole and the spring is evenly stressed, avoiding air leakage or abnormal wear of the valve plate due to assembly errors, and improving reliability.

[0037] An ultra-thin exhaust valve plate 6 is used, with a thickness of 0.12mm-0.13mm, reducing the thickness from the traditional 0.152mm to 0.12-0.13mm (e.g., 0.127mm). Performance is closely related to the valve plate stiffness; the lower the stiffness of the exhaust valve plate 6, the easier it is to open, and the less compression work is required. The calculation formula for the spring design is as follows:

[0038] Where K is stiffness, E is elastic modulus, b is spring width, h is spring thickness, and L is spring length, which in valve plate design is the arm length, the distance from the pressing edge of the limiting plate 4 to the center of the valve head. From the above formula, it can be seen that the smaller the thickness, the smaller the stiffness. In this embodiment, the thickness of the exhaust valve plate 6 is 0.127mm, compared to the current minimum thickness of 0.152mm for conventional piston compressors, representing a 17% reduction in thickness and a 42% reduction in stiffness. Simulation and actual measurements show a 2% performance improvement.

[0039] One end of the exhaust valve spring 5 is pressed and constrained between the limiting plate 4 and the exhaust valve plate 6, while the other end extends towards the exhaust port to form a cantilever structure, which is used to contact the exhaust valve plate 6. One end of the exhaust valve plate 6 is pressed and constrained between the exhaust valve spring 5 and the valve plate 7, while the other end extends towards the exhaust port to form a cantilever structure, which is used to block the exhaust port.

[0040] like Figure 5 The diagram shows the installation of the exhaust side components. Before installation, the exhaust valve spring 5 has a deflection of 10°. After installation, the exhaust spring is tightly attached to the limiting plate 4, at which point the deflection is 6%. Therefore, the exhaust spring has an upward force. Before the exhaust valve plate 6 reaches its higher lift, the exhaust valve plate 6 will not be subjected to a large spring force from the exhaust valve spring 5. It can also be observed that due to the structural limitation of the limiting plate 4, the limiting plate 4 and the exhaust valve spring 5 are not fitted together at the upper end of the exhaust port. This is to allow for some upward space when the exhaust valve plate 6 strikes the exhaust valve spring 5, reducing the stress during the strike. Simultaneously, at the highest point, the exhaust valve spring 5 stores a certain amount of downward spring energy, which helps the exhaust valve plate 6 close quickly, reducing exhaust backflow and increasing cooling capacity.

[0041] The cantilever structure makes the exhaust valve plate 6 and exhaust valve spring 5 easy to bend under force, resulting in low opening resistance; the spring deflection design ensures that the spring is still under relatively low force when the valve plate is opened to its maximum lift, reducing obstruction to the valve plate; at the same time, when the valve plate is closed, the spring elastically returns to push the valve plate to seal quickly, reducing exhaust backflow.

[0042] like Figure 6 As shown, an exhaust high-pressure ring is provided outside the opening at the end of the exhaust port away from the cylinder, protruding from the bottom surface of the groove of the valve plate 7. The exhaust high-pressure ring abuts against the exhaust valve plate 6. Both the outer circle and the inner circle at one end of the exhaust high-pressure ring are made with arc transition surfaces, and an end plane is provided between the outer circle and the inner circle.

[0043] Specifically, the exhaust high-pressure ring features an arc-shaped valve orifice, with 0.8mm radius arc surfaces on both sides and a 0.2mm flat surface in the middle. This design serves two purposes: first, it reduces the viscous force when the exhaust valve plate 6 opens, improving efficiency, especially at low speeds; second, it enhances reliability. Under normal circumstances, the exhaust valve plate 6 strikes the valve orifice with point contact. When the exhaust high-pressure ring has a flat valve orifice, the same point receives a large impact when the exhaust valve plate 6 strikes the valve orifice. However, with the arc-shaped valve orifice, multiple points receive a large impact when the exhaust valve plate 6 strikes the valve orifice, thus significantly increasing the fatigue life of individual points. Through simulation and actual testing, performance is improved by 2%, and reliability by 50%.

[0044] Example 2 In another typical embodiment of this utility model, such as Figures 1-6As shown, a compressor is presented.

[0045] By utilizing the compressor valve group as in Example 1, the compressor valve group features an expanded suction port 11 and optimized exhaust valve plate 6 stiffness design, which increases the compressor's suction volume, reduces compression work, and improves refrigeration efficiency. The actual performance is improved by more than 2%, meeting the "high energy efficiency" requirement of inverter refrigerators.

[0046] Leveraging the compatibility of the compressor valve assembly with existing components, the compressor does not require the creation of new molds to produce core components. Performance upgrades can be achieved simply by replacing the compressor valve assembly, making it suitable for mass production and iteration of older models.

[0047] 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 compressor valve assembly, characterized in that, The device includes an intake valve plate, a valve plate, an exhaust valve plate, an exhaust valve spring, and a limiting plate arranged sequentially. The valve plate has an intake hole and an exhaust hole. The intake hole is offset towards the center of the cylinder bore at the end closer to the cylinder than at the other end, and the opening diameter of the intake hole at the end closer to the cylinder is larger than the opening diameter at the other end. The intake valve plate cooperates to block the opening of the intake hole at the end closer to the cylinder. The valve plate has a valve plate groove on the side away from the cylinder. The exhaust valve plate, exhaust valve spring, and limiting plate cooperate with the valve plate groove. The exhaust valve plate cooperates to block the opening of the exhaust hole at the end away from the cylinder. The exhaust valve spring abuts against the limiting plate to receive the thrust applied when the exhaust valve plate opens and undergoes elastic deformation.

2. The compressor valve assembly as described in claim 1, characterized in that, The intake valve plate is inclined relative to the side of the valve plate to avoid the exhaust port.

3. The compressor valve assembly as described in claim 1 or 2, characterized in that, The front end of the suction valve plate, which mates with the suction hole, is positioned as the suction valve tongue. A contraction section is provided between the tail end of the suction valve plate and the suction valve tongue.

4. The compressor valve assembly as described in claim 1, characterized in that, The valve plate groove extends to the tail end with an anti-fooling groove, and the exhaust valve plate and exhaust valve spring are provided with protrusions at their tail ends to insert into the anti-fooling groove and constrain the position of the exhaust valve plate and exhaust valve spring.

5. The compressor valve assembly as described in claim 1 or 4, characterized in that, The thickness of the exhaust valve plate is 0.12mm-0.13mm.

6. The compressor valve assembly as described in claim 1, characterized in that, One end of the exhaust valve spring is pressed and constrained between the limiting plate and the exhaust valve plate, while the other end extends towards the exhaust hole to form a cantilever structure, which is used to contact the exhaust valve plate.

7. The compressor valve assembly as described in claim 6, characterized in that, One end of the exhaust valve plate is pressed and constrained between the exhaust valve spring and the valve plate, while the other end extends towards the exhaust port to form a cantilever structure, which is used to block the exhaust port.

8. The compressor valve assembly as described in claim 1, characterized in that, The exhaust port is provided with an exhaust high-pressure ring protruding from the bottom surface of the valve plate groove at the end away from the cylinder, and the exhaust high-pressure ring abuts against the exhaust valve plate.

9. The compressor valve assembly as described in claim 8, characterized in that, Both the outer and inner circles of the exhaust high-pressure ring have arc transition surfaces, and an end plane is provided between the outer and inner circles.

10. A compressor, characterized in that, The compressor valve assembly is used as described in any one of claims 1-9.

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