Air cylinder, compressor and refrigeration equipment

Abstract

The invention discloses an air cylinder, a compressor and refrigeration equipment, and relates to the technical field of compressors, the air cylinder comprises a cylinder body and an exhaust notch, the cylinder body is provided with a compression cavity, and the air cylinder is provided with an axial section passing through the central axis of the air cylinder; the exhaust notch is formed in the side wall of the compression cavity and used for being communicated with an exhaust hole of an adjacent component, a first contour line, intersecting with the axial section of the air cylinder, of the exhaust notch is an arc curve, and the circle center of the first contour line is located on the side, close to the center of the compression cavity, of the bottom of the exhaust hole; according to the technical scheme, the energy efficiency of the compressor can be improved.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and particularly to a cylinder, compressor, and refrigeration equipment. Background Technology

[0002] In existing rotary compressors, the upper cylinder end face is usually machined with an exhaust slit, and the corresponding position of the upper bearing has an exhaust port. At the end of compression, the high-pressure refrigerant flows sequentially through the exhaust slit and the bearing exhaust port before entering the housing.

[0003] Existing exhaust ports generally adopt the "oblique cut" form—that is, a cavity formed by the intersection of two cylindrical surfaces with their axes inclined at opposite directions. However, this geometry inevitably forms a minimum flow cross section near the intersection of the two cylindrical surfaces. This cross section area becomes the "throat" that restricts sudden increases in flow rate throughout the exhaust process, which is not conducive to improving compressor energy efficiency. Summary of the Invention

[0004] The main objective of this invention is to provide a cylinder, compressor, and refrigeration equipment that aims to improve the energy efficiency of the compressor.

[0005] To achieve the above objectives, the present invention provides a cylinder for use in a compressor, the cylinder comprising: The cylinder body is provided with a compression chamber, and the cylinder has an axial section passing through its central axis; An exhaust vent is provided on the side wall of the compression chamber and is used to connect the exhaust ports of adjacent components. The first contour line of the exhaust vent intersecting the axial section of the cylinder is an arc curve, and the center of the first contour line is located on the side of the bottom of the exhaust port near the center of the compression chamber.

[0006] In one embodiment, the second contour line where the exhaust cut intersects the radial section of the cylinder is a curve.

[0007] In one embodiment, the second contour line is a circular arc curve.

[0008] In one embodiment, the second contour line includes a first arc segment, an intermediate segment, and a second arc segment connected in sequence, wherein the radius of curvature of the first arc segment or the second arc segment is different from the radius of curvature of the intermediate segment.

[0009] In one embodiment, the minimum radius of curvature of the exhaust port is R, and the equivalent radius of curvature of the second contour line is R1, where 0.8R ≤ R1 ≤ 1.2R; And / or, the radius of curvature of the intermediate segment is R2, where R≤R2≤1.2R.

[0010] In one embodiment, the first arc segment and the second arc segment are symmetrically arranged about the middle segment.

[0011] In one embodiment, the radius of the first contour line is smaller than the minimum diameter of the vent hole.

[0012] The present invention also proposes a compressor comprising an upper bearing and an upper cylinder, wherein the upper cylinder is a cylinder as described above, and the upper bearing is disposed above the cylinder and has the exhaust port formed thereon.

[0013] In one embodiment, the compressor further includes an exhaust valve plate and a lift limiter, the exhaust valve plate covering the exhaust port, and the lift limiter being disposed on the back of the exhaust valve plate and used to restrict the opening stroke of the exhaust valve plate; The minimum diameter of the exhaust port is D, and the maximum lift of the lift limiter is h, where h > D / 4.

[0014] The present invention also proposes a refrigeration device, which includes a compressor as described above.

[0015] In the technical solution of this invention, the cylinder has an axial section passing through its central axis. Compared to designing the first contour line where the exhaust port intersects the axial section of the cylinder as a straight line, which results in a minimum flow cross section and throttling, this invention designs the first contour line where the exhaust port intersects the axial section of the cylinder as an arc curve, and the center of the first contour line is located on the side of the bottom of the exhaust port near the center of the compression chamber. This ensures that the flow area of ​​each cross section in the gas flow direction remains consistent, thereby making full use of the clearance volume, reducing the clearance ratio of the cylinder, and also helping to ensure smooth exhaust, which can reduce exhaust resistance and thus improve the capacity and energy efficiency of the compressor, especially under low-frequency conditions. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of a cylinder according to an embodiment of the present invention; Figure 2 This is a schematic diagram showing the location of the exhaust inlet and exhaust port; Figure 3 This is a schematic diagram of the exhaust port structure; Figure 4 This is a top view of the exhaust port. Figure 5 This is a schematic diagram of the assembly of the cylinder and bearing; Figure 6 This is a cross-sectional view of the cylinder and bearing assembly. Figure 7 This is a schematic diagram of the pump body assembly in an embodiment of the compressor provided by the present invention.

[0018] Explanation of icon numbers: 10. Cylinder; 11. Cylinder block; 111. Compression chamber; 112. Exhaust port; 12. First contour line; 13. Second contour line; 131. First arc segment; 132. Middle section; 133. Second arc segment; 20. Upper bearing; 21. Vent hole; 30. Exhaust valve plate; 40. Lower cylinder; 50. Lower bearing.

[0019] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0021] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0022] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0023] In existing rotary compressors, the upper cylinder end face is usually machined with an exhaust slit, and the corresponding position of the upper bearing has an exhaust port. At the end of compression, the high-pressure refrigerant flows sequentially through the exhaust slit and the bearing exhaust port before entering the housing.

[0024] Existing exhaust ports generally adopt a "beveled cut" design—a cavity formed by the intersection of two cylindrical surfaces with relatively inclined axes. However, this geometry inevitably forms a minimum flow cross-section near the intersection of the two cylindrical surfaces. This cross-sectional area becomes the "throat" that restricts sudden increases in flow rate throughout the exhaust process. Even more disadvantageous is that the irregular transition region formed between the beveled cut and the cylinder and bearings retains a large amount of high-pressure refrigerant after exhaust, creating an ineffective clearance volume. This gas re-expands during the subsequent intake stroke, occupying effective intake volume and directly reducing volumetric efficiency. Furthermore, this ineffective volume does not contribute additional flow during the exhaust phase; it only increases clearance and re-expansion losses, thus affecting compressor efficiency.

[0025] To solve this technical problem, the present invention proposes a cylinder 10, which is applied to a compressor.

[0026] Please see Figure 1 and Figure 6 In one embodiment of the present invention, the cylinder 10 includes a cylinder body 11 and an exhaust port 112. The cylinder body 11 is provided with a compression chamber 111. The cylinder 10 has an axial section passing through its central axis. The exhaust port 112 is provided on the side wall of the compression chamber 111 and is used to connect the exhaust port 21 of an adjacent component. The first contour line 12 intersecting the axial section of the cylinder 10 is an arc curve, and the center of the first contour line 12 is located on the side of the bottom of the exhaust port 21 near the center of the compression chamber 111. This improves the overall energy efficiency of the compressor.

[0027] In the technical solution of this invention, the cylinder 10 has an axial section passing through its central axis. Compared to designing the first contour line 12, which intersects the exhaust port 112 and the axial section of the cylinder 10, as a straight line, resulting in a minimum flow cross section and throttling, this invention designs the first contour line 12, which intersects the exhaust port 112 and the axial section of the cylinder 10, as an arc curve. The center of the first contour line 12 is located on the side of the bottom of the exhaust port 21 near the center of the compression chamber 111. This ensures that the flow area of ​​each section in the gas flow direction remains consistent, thereby making full use of the clearance volume, reducing the clearance ratio of the cylinder 10, and also helping to ensure smooth exhaust, reducing exhaust resistance, and thus improving the capacity and energy efficiency of the compressor, especially under low-frequency operating conditions.

[0028] It should be noted that the "cross section" in "flow area of ​​each cross section" refers to a plane perpendicular to the axial direction, intercepted along the direction of gas flow. The center of the compression chamber 111 of the cylinder 10 is specifically the core position where the gas compression process takes place inside the cylinder 10, located in the central region of the cylinder 10's axial direction.

[0029] When the shape of the exhaust port 21 is not limited, for example, the exhaust port 21 can be configured as a constant diameter exhaust port 21 or a variable diameter exhaust port 21, the diameter of the exhaust port 21 on the side closest to the cylinder 10 shall be used as the standard. Figure 2 and Figure 6 As shown, the center O of the first contour line 12 is set on the side of the bottom of the exhaust port 21 near the center of the compression chamber 111. The distance from any point on the same first contour line 12 to the center is equal, which makes the flow area of ​​each section in the entire flow channel from the compression chamber 111 to the exhaust port 21 the same. That is, there is no minimum flow area for throttling, and all are the maximum exhaust flow areas. At this time, the ratio of the flow area to the clearance volume can reach the maximum value, thereby effectively reducing the resistance in the exhaust process, reducing the over-compression phenomenon inside the compression chamber 111, and improving the overall working efficiency.

[0030] Because the inner wall of cylinder 10 is designed with a curved shape, and the bottom of exhaust port 21 also adopts a curved design, this geometric characteristic causes the radius of curvature of the inner wall profile (first contour line 12) of exhaust cut 112 to show significant differences when viewed in different cross-sectional views. Specifically, as the cross-sectional position changes, the radius of curvature of the first contour line 12 of exhaust cut 112 will change accordingly, resulting in different clearance volumes for that part. In order to maximize the ratio of flow area to clearance volume in practical applications and optimize the utilization efficiency of the internal space of cylinder 10, it is necessary to conduct detailed analysis and adjustment of the second contour line 13, which intersects the radial section of exhaust cut 112 and cylinder 10.

[0031] Optionally, in an embodiment of the present invention, the second contour line 13 where the exhaust cut 112 intersects the radial section of the cylinder 10 is a curve. This curve can be a circular arc or a combination of multiple arcs. The radial section can be the end face of the cylinder 10.

[0032] When the curve is a circular arc, its radius can be reasonably set according to the specific specifications and design requirements of the cylinder 10 to ensure the smoothness and stability of the exhaust process. When the curve is a combination of multiple arcs, the transitions between the arcs must be smooth to avoid sharp turning points, thereby reducing energy loss during gas flow and further improving the working performance of the cylinder 10.

[0033] Furthermore, since the flow area of ​​each cross section is the same throughout the gas flow path from the compression chamber 111 to the exhaust port 21, the distance Rc from the intersection point of the first profile line 12 and the second profile line 13 to the center of the circle is equal to the radius of curvature Ra of the first profile line 12.

[0034] Please see Figures 3 to 4 In an embodiment of the present invention, the second contour line 13 includes a first arc segment 131, a middle segment 132 and a second arc segment 133 connected in sequence, wherein the radius of curvature of the first arc segment 131 or the second arc segment 133 is different from the radius of curvature of the middle segment 132.

[0035] Understandably, the second contour line 13 is composed of multiple arc segments. By adjusting the curvature, length, and relative position of each arc, the flow direction and velocity distribution of gas during exhaust can be precisely controlled. For example, in areas where high exhaust velocity is required, arcs with larger curvature and shorter lengths can be used to accelerate the exhaust speed; while in areas where smooth exhaust is required, arcs with smaller curvature and longer lengths are used to allow the gas to pass through the exhaust cut-out 112 more stably.

[0036] Specifically, in the embodiments of the present invention, the minimum radius of curvature of the exhaust port 21 is R, and the equivalent radius of curvature of the second profile line 13 is R1, where 0.8R ≤ R1 ≤ 1.2R. It can be understood that when R1 is less than 0.8R, the equivalent radius of curvature of the second profile line 13 is too small, and the cross-sectional area of ​​the exhaust channel from the exhaust cut 112 to the exhaust port 21 changes too quickly, which will cause the gas to suddenly accelerate and decelerate when entering the exhaust port 21, thereby generating turbulence and eddies, increasing the flow resistance of the gas, and reducing the exhaust efficiency. When R1 is greater than 1.2R, the equivalent radius of curvature of the second profile line 13 is too large, and the cross-sectional area of ​​the exhaust channel from the exhaust cut 112 to the exhaust port 21 changes too slowly, which is not conducive to the rapid discharge of gas during the exhaust process and affects the exhaust efficiency.

[0037] Therefore, limiting the equivalent radius of curvature R1 of the second profile 13 to between 0.8R and 1.2R can effectively guide the gas to flow more smoothly, reduce the generation of turbulence and eddies, thereby reducing flow resistance and improving exhaust efficiency.

[0038] The specific values ​​of the equivalent radius of curvature R1 of the second contour line 13 include, but are not limited to, 0.8R, 0.9R, R, 1.1R, and 1.2R. However, in other embodiments, while ensuring exhaust efficiency, the equivalent radius of curvature R1 of the second contour line 13 can be greater than 1.2R or less than 0.8R.

[0039] It should be noted that the equivalent radius of curvature of the second contour line 13 is R1. This represents a representative radius of curvature value obtained by comprehensively considering the curvature of each arc segment and their proportion within the entire second contour line 13. This equivalent radius of curvature R accurately reflects the overall curvature of the second contour line 13. During the exhaust process, it has a specific proportional relationship with the minimum radius of curvature R1 of the exhaust port 21, namely 0.8R ≤ R1 ≤ 1.2R. This setting can better optimize the exhaust effect, ensuring that the gas is discharged according to the expected flow direction and velocity distribution when passing through the exhaust cut-out 112, thus meeting the exhaust requirements of the compressor under different operating conditions.

[0040] Furthermore, in an embodiment of the present invention, the radius of curvature of the intermediate section 132 is R2, where R ≤ R2 ≤ 1.2R. By limiting the radius of curvature R2 of the intermediate section 132 to between R and 1.2R, the smooth flow of air at the exhaust cut-out 112 can be effectively promoted, significantly reducing flow resistance and the probability of turbulence and eddies. This not only helps to improve exhaust efficiency, making gas emission more efficient, but also significantly reduces energy loss of gas during the exhaust process, ensuring efficient energy utilization. Simultaneously, it improves the stability and uniformity of the exhaust, avoiding performance fluctuations caused by unstable airflow, thereby enhancing the compressor's capacity and energy efficiency.

[0041] The specific value of the radius of curvature R2 of the middle segment 132 includes, but is not limited to, R, 1.1R, and 1.2R. However, in other embodiments, while ensuring overall performance, the radius of curvature R2 of the middle segment 132 can be greater than 1.2R or less than R.

[0042] Optionally, in an embodiment of the present invention, the first arc segment 131 and the second arc segment 133 are symmetrically arranged about the middle segment 132. This reduces the airflow resistance at the exhaust cut-out 112, ensuring that the airflow can flow smoothly out of the exhaust cut-out 112, thereby improving exhaust efficiency, reducing energy loss, and improving the pneumatic performance of the cylinder 10.

[0043] Please see Figure 2 and Figure 6In an embodiment of the present invention, the radius of the first contour line 12 is smaller than the minimum diameter of the exhaust port 21, which is the diameter of the bottom exhaust port 21 on the side of the exhaust port 21 closest to the cylinder 10. Since the radius of the first contour line 12 is smaller than the minimum radius of the exhaust port 21, the flow area of ​​the exhaust cut 112 on the end face of the cylinder 10 is smaller than the flow area of ​​the exhaust port 21. This optimizes the gas exhaust process, reduces turbulence and eddies during the exhaust process, and lowers the energy consumption of the compressor. It also reduces pressure fluctuations during the exhaust process, protecting other components in the exhaust system, thereby improving overall exhaust efficiency and service life. However, this design is not limited to this. In other embodiments, based on the fact that the flow area of ​​each cross-section in the entire flow channel from the compression chamber 111 to the exhaust port 21 is the same, the minimum radius of the exhaust port 21 can be equal to the radius of the first contour line 12.

[0044] The present invention also proposes a compressor comprising an upper bearing 20 and an upper cylinder 10. The specific structure of the upper cylinder 10 is as described in the above embodiments. Since this compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. The upper bearing 20 is located above the cylinder 10 and has the exhaust port 21 formed thereon.

[0045] Specifically, the compressor can be configured as a rotary compressor, which includes a stator assembly and a pump body assembly, such as... Figure 5 and Figure 7 As shown, the pump assembly includes an upper bearing 20, a lower bearing 50, at least one cylinder 10 disposed between the upper bearing 20 and the lower bearing 50, and a crankshaft passing through the upper bearing 20, the cylinder 10, and the lower bearing 50. The crankshaft is connected to a rotor assembly that mates with the stator assembly. The crankshaft is driven to rotate by the cooperation of the stator assembly and the rotor assembly, thereby compressing the gas. When the rotary compressor is a twin-cylinder compressor, there are two cylinders 10, namely an upper cylinder 10 and a lower cylinder 40, with a partition sandwiched between the upper cylinder 10 and the lower cylinder 40.

[0046] Optionally, in an embodiment of the present invention, the compressor further includes an exhaust valve plate 30 and a lift limiter. The exhaust valve plate 30 covers the exhaust port 21, and the lift limiter is disposed on the back of the exhaust valve plate 30 and is used to constrain the opening stroke of the exhaust valve plate 30. The minimum diameter of the exhaust port 21 is D, and the maximum lift of the lift limiter is h, where h>D / 4.

[0047] Understandably, since the exhaust port 21 is located on the upper bearing 20 and the exhaust valve plate 30 is located on the upper bearing 20 and is set accordingly to the exhaust port 21, when the air pressure in the cylinder 10 is greater than the exhaust air pressure, the exhaust valve plate 30 opens, and the high-pressure refrigerant passes through the exhaust port 112 and is discharged from the exhaust port 21.

[0048] The lift limiter is installed on the upper bearing 20 and located on the back of the exhaust valve plate 30. The lift limiter can constrain the opening stroke of the exhaust valve port, and the maximum lift h of the lift limiter satisfies: h>D / 4. Combined with the cooperation of the exhaust valve plate 30 and the lift limiter, it can ensure that the exhaust valve plate 30 will not interfere with other internal components of the compressor due to excessive opening during the opening process, thus ensuring the stable operation of the compressor, extending the service life of the compressor, and making the exhaust process smoother and reducing energy loss. Specifically, when applied to refrigeration equipment, this compressor effectively improves refrigeration efficiency. Under varying workloads, the compressor dynamically adjusts its discharge state through the coordinated action of the discharge valve 30 and the lift limiter. During low-load operation, the discharge valve 30 opens only slightly, and the lift limiter effectively restricts its stroke, preventing unnecessary energy loss and reducing energy consumption. Conversely, during high-load operation, the discharge valve 30 opens fully to meet the refrigeration equipment's demand for a large amount of cooling output, ensuring optimal cooling performance. Furthermore, it helps reduce compressor noise and vibration, providing a quieter and more stable operating environment for the refrigeration equipment and enhancing the user experience.

[0049] The present invention also proposes a refrigeration device, which includes a compressor. The specific structure of the compressor is as described in the above embodiments. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0050] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.

Claims

1. A cylinder used in a compressor, characterized in that, include: The cylinder body is provided with a compression chamber, and the cylinder has an axial section passing through its central axis; An exhaust vent is provided on the side wall of the compression chamber and is used to connect the exhaust ports of adjacent components. The first contour line of the exhaust vent intersecting the axial section of the cylinder is an arc curve, and the center of the first contour line is located on the side of the bottom of the exhaust port near the center of the compression chamber.

2. The cylinder as described in claim 1, characterized in that, The second contour line where the exhaust cut intersects the radial section of the cylinder is a curve.

3. The cylinder as described in claim 2, characterized in that, The second contour line is a circular arc curve.

4. The cylinder as described in claim 2, characterized in that, The second contour line includes a first arc segment, a middle segment, and a second arc segment connected in sequence, wherein the radius of curvature of the first arc segment or the second arc segment is different from the radius of curvature of the middle segment.

5. The cylinder as described in claim 4, characterized in that, The minimum radius of curvature of the exhaust port is R, and the equivalent radius of curvature of the second contour line is R1, where 0.8R≤R1≤1.2R; And / or, the radius of curvature of the intermediate segment is R2, where R≤R2≤1.2R.

6. The cylinder as described in claim 5, characterized in that, The first arc segment and the second arc segment are symmetrically arranged about the middle segment.

7. The cylinder as described in claim 1, characterized in that, The radius of the first contour line is smaller than the minimum diameter of the vent hole.

8. A compressor, characterized in that, It includes an upper bearing and an upper cylinder, wherein the upper cylinder is a cylinder as described in any one of claims 1 to 7, the upper bearing is disposed above the cylinder and has the exhaust port formed thereon.

9. The compressor as claimed in claim 8, characterized in that, The compressor also includes an exhaust valve plate and a lift limiter. The exhaust valve plate covers the exhaust port, and the lift limiter is located on the back of the exhaust valve plate and is used to limit the opening stroke of the exhaust valve plate. The minimum diameter of the exhaust port is D, and the maximum lift of the lift limiter is h, where h > D / 4.

10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 8 to 9.

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