Air cylinder for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses an air cylinder for a compressor. The air cylinder comprises a cylinder body and a first one-way conduction structure, the cylinder body is provided with an air suction port, an air suction channel and a cylinder body inner cavity, and the air suction channel communicates with the air suction port and the cylinder body inner cavity; the first one-way conduction structure is arranged in the air suction channel, and the conduction direction of the first one-way conduction structure is from the air suction port to the inner cavity of the cylinder body. Reverse flowing suction airflow can be stored through the suction channel, and the suction airflow is prevented from flowing back to the suction port from the inner cavity of the cylinder body. A first one-way conduction structure is arranged in the air suction channel, air suction airflow is allowed to flow forwards from the air suction opening to the inner cavity of the cylinder body, and the air suction airflow can be prevented from flowing reversely from the inner cavity of the cylinder body to the air suction opening. In this way, suction airflow can be effectively prevented from flowing back to the suction port from the inner cavity of the cylinder body, suction pulsation is kept in a stable state, the suction capacity of the compressor is prevented from being affected, and therefore the capacity of the compressor can be improved. The utility model further discloses the compressor.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and particularly relates to a cylinder for a compressor and a compressor. Background Art

[0002] At present, there is a situation where the exhaust gas flow in a rotary compressor flows back from the exhaust valve to the cylinder compression chamber. The backflow of the exhaust gas flow will cause changes in the gas flow pulsation in the compression chamber, and the exhaust volume of the compressor will decrease. The backflow gas is repeatedly compressed in the compression chamber, resulting in a decrease in the energy efficiency of the compressor.

[0003] In order to improve the energy efficiency of the compressor, a compressor is disclosed in the related art, by providing a one-way conduction structure in the exhaust route of the compressor to prevent the refrigerant discharged from the compressor exhaust from flowing back to the compressor.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

[0005] The related art can reduce the exhaust loss at high speeds, but when the rotary compressor reaches the end of the suction stroke, there is a situation where the suction gas flow flows back from the cylinder suction port to the suction passage. The impact of the backflow gas flow causes changes in the suction gas flow pulsation, which will also affect the compressor capacity.

[0006] It should be noted that the information disclosed in the above background art section is only used to enhance the understanding of the background of the present application, and thus may include information that does not constitute the prior art known to those of ordinary skill in the art. Summary of the Utility Model

[0007] To have a basic understanding of some aspects of the disclosed embodiments, a simple summary is given below. The summary is not a general review, nor is it intended to identify key / important constituent elements or delineate the protection scope of these embodiments, but rather serves as a preface to the subsequent detailed description.

[0008] The embodiments of the present disclosure provide a cylinder for a compressor and a compressor to prevent the suction gas flow of the cylinder from flowing back and improve the compressor capacity.

[0009] According to the first aspect of the embodiments of the present utility model, a cylinder for a compressor is provided, including: a cylinder block, provided with a suction port, a suction passage and a cylinder inner cavity, the suction passage communicating the suction port and the cylinder inner cavity, and a first one-way conduction structure provided in the suction passage, the conduction direction of the first one-way conduction structure being from the suction port to the cylinder inner cavity.

[0010] Optionally, the first one-way conduction structure includes a first Tesla valve channel, and the first Tesla valve channel includes: a first main channel, arranged along the extending direction of the intake channel to connect the intake port and the inner cavity of the cylinder; a first branch channel, which is arc-shaped and bent, and both ends of the first branch channel are connected to the side wall of the first main channel to form a resistance channel; wherein, along the direction from the intake port towards the inner cavity of the cylinder, the intake air flow flows along the first main channel; along the direction from the inner cavity of the cylinder towards the intake port, the intake air flow can flow into the first branch channel to form a diversion, so as to prevent the intake air flow from flowing from the inner cavity of the cylinder towards the intake port.

[0011] Optionally, the first Tesla valve channel includes a plurality of first branch channels, and the plurality of first branch channels are relatively arranged on both sides of the first main channel; and / or, the first Tesla valve channel includes a plurality of first branch channels, and the plurality of first branch channels are arranged at intervals along the extending direction of the first main channel.

[0012] Optionally, the ratio range between the volume of the first Tesla valve channel and the cylinder displacement is greater than or equal to 0.02 and less than or equal to 0.1.

[0013] Optionally, the end face of the cylinder along the cylinder axis is provided with an intake inclined notch, and the intake inclined notch connects the intake channel and the inner cavity of the cylinder to guide the intake air flow to flow from the intake channel to the inner cavity of the cylinder; wherein, along the direction from the intake channel towards the inner cavity of the cylinder, the diameter of the intake inclined notch gradually increases.

[0014] Optionally, the cylinder is further provided with a sliding vane groove, and the angular range between the center line of the intake inclined notch and the center line of the sliding vane groove along the circumferential direction of the cylinder is greater than or equal to 5° and less than or equal to 23°.

[0015] Optionally, the cylinder is further provided with an exhaust channel and an exhaust port, the exhaust channel connects the inner cavity of the cylinder and the exhaust port, and the exhaust channel is provided with a second one-way valve structure, and the conduction direction of the second one-way valve structure is from the inner cavity of the cylinder to the exhaust port.

[0016] Optionally, the second one-way valve structure includes a second Tesla valve channel, and the second Tesla valve channel includes: a second main channel, arranged along the extending direction of the exhaust channel to connect the inner cavity of the cylinder and the exhaust port; a second branch channel, which is arc-shaped and bent, and both ends of the second branch channel are connected to the side wall of the second main channel to form a resistance channel; wherein, along the direction from the inner cavity of the cylinder towards the exhaust port, the exhaust air flow flows along the second main channel; along the direction from the exhaust port towards the inner cavity of the cylinder, the exhaust air flow flows into the second branch channel to form a diversion, so as to prevent the exhaust air flow from flowing from the exhaust port towards the inner cavity of the cylinder.

[0017] Optionally, the ratio range between the volume of the second Tesla valve channel and the cylinder displacement is greater than or equal to 0.01 and less than or equal to 0.02.

[0018] Optionally, an exhaust inclined cut is provided on the end face of the cylinder block along the axial direction of the cylinder. The exhaust inclined cut communicates the inner cavity of the cylinder block with the exhaust passage to guide the exhaust gas flow from the inner cavity of the cylinder block to the exhaust passage. Among them, along the direction from the inner cavity of the cylinder block towards the exhaust passage, the caliber of the exhaust inclined cut gradually decreases.

[0019] Optionally, the cylinder block is further provided with a sliding vane groove. Along the circumferential direction of the cylinder, the angle range between the center line of the exhaust inclined cut and the center line of the sliding vane groove is greater than or equal to 5° and less than or equal to 15°.

[0020] According to the second aspect of the embodiments of the present invention, a compressor is provided, including a cylinder for a compressor as described in any one of the above embodiments.

[0021] The cylinder for a compressor and the compressor provided by the embodiments of the present disclosure can achieve the following technical effects:

[0022] An air intake passage communicating the air intake port and the inner cavity of the cylinder block is provided in the cylinder block, so that the air intake port is not directly communicated with the inner cavity of the cylinder block. The air intake passage can store the reversely flowing air intake gas flow and prevent the air intake gas flow from flowing back from the inner cavity of the cylinder block to the air intake port. A first one-way conduction structure is provided in the air intake passage, allowing the air intake gas flow to flow forward from the air intake port towards the inner cavity of the cylinder block and preventing the air intake gas flow from flowing reversely from the inner cavity of the cylinder block towards the air intake port. By providing an air intake passage between the air intake port and the inner cavity of the cylinder block and a first one-way conduction structure in the air intake passage, it can effectively prevent the air intake gas flow from flowing back from the inner cavity of the cylinder block to the air intake port. In this way, the air intake pulsation can be kept in a relatively stable state, avoiding the influence on the air intake volume of the compressor, and thus improving the compressor capacity.

[0023] The above general description and the following description are only exemplary and explanatory, and are not used to limit the present application. Description of the Drawings

[0024] One or more embodiments are exemplarily illustrated by corresponding drawings. These exemplary illustrations and the drawings do not constitute limitations on the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a proportional limitation, and among them:

[0025] Figure 1 is a schematic structural diagram of a cylinder provided by an embodiment of the present disclosure;

[0026] Figure 2 is a schematic structural diagram of another cylinder provided by an embodiment of the present disclosure;

[0027] Figure 3 is Figure 2 an enlarged schematic view of part A shown;

[0028] Figure 4 isFigure 2 An enlarged schematic view of part B shown

[0029] Figure 5 It is a schematic structural diagram of another cylinder provided by an embodiment of the present disclosure;

[0030] Figure 6 It is a schematic structural diagram of another cylinder provided by an embodiment of the present disclosure;

[0031] Figure 7 It is an exploded schematic view of a pump body assembly provided by an embodiment of the present disclosure.

[0032] Reference numerals:

[0033] 10: Cylinder;

[0034] 20: Cylinder block; 21: Suction port; 22: Inner cavity of the cylinder; 23: End face; 231: Upper end face; 232: Lower end face; 24: Suction inclined notch; 241: Center line of the suction inclined notch; 242: First suction inclined notch; 243: Second suction inclined notch; 25: Vane slot; 251: Center line of the vane slot; 26: Exhaust port; 27: Exhaust inclined notch; 271: Center line of the exhaust inclined notch;

[0035] 30: Suction channel; 301: First suction channel; 302: Second suction channel; 31: First one-way conduction structure; 32: First Tesla valve channel; 33: First main flow channel; 34: First branch flow channel; 35: Blocking block;

[0036] 40: Exhaust channel; 41: Second one-way valve structure; 42: Second Tesla valve channel; 43: Second main flow channel; 44: Second branch flow channel;

[0037] 50: Bearing; 51: Main bearing; 52: Sub-bearing;

[0038] 60: Pump body assembly. Detailed implementation manners

[0039] In order to be able to understand the features and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are only for reference and explanation purposes and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, multiple details are provided to provide a full understanding of the disclosed embodiments. However, one or more embodiments can still be implemented without these details. In other cases, well-known structures and devices can be shown in a simplified manner to simplify the drawings.

[0040] In the description, claims, and above-mentioned drawings of the embodiments of the present disclosure, terms such as "first" and "second" are used to distinguish similar objects, and do not necessarily describe a specific order or sequence. It should be understood that the data used in this way can be interchanged under appropriate circumstances, so as to describe the embodiments of the present disclosure herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusion.

[0041] In the embodiments of the present disclosure, the orientation or positional relationship indicated by terms such as "upper", "lower", "inner", "middle", "outer", "front", and "back" is based on the orientation or positional relationship shown in the drawings. These terms are mainly used to better describe the embodiments of the present disclosure and their embodiments, and are not used to limit that the indicated devices, elements, or components must have a specific orientation, or be constructed and operated in a specific orientation. And, in addition to being able to represent the orientation or positional relationship, some of the above terms may also be used to represent other meanings. For example, the term "upper" may also be used to represent a certain attachment relationship or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0042] In addition, the terms "arrangement", "connection", and "fixation" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or there is internal communication between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0043] Unless otherwise specified, the term "plurality" means two or more.

[0044] In the embodiments of the present disclosure, the character " / " indicates that the front and rear objects are in an "or" relationship. For example, A / B means: A or B.

[0045] The term "and / or" is a description of the associated relationship of an object, indicating that three relationships can exist. For example, A and / or B means: A or B, or, the three relationships of A and B.

[0046] It should be noted that, without conflict, the embodiments in the embodiments of the present disclosure and the features in the embodiments can be combined with each other.

[0047] Combined with Figures 1-7 As shown, the embodiments of the present disclosure provide a cylinder 10 for a compressor, including a cylinder block 20 and a first one-way conduction structure 31.

[0048] The cylinder block 20 is provided with an air inlet 21, an air intake passage 30, and a cylinder inner cavity 22. The air intake passage 30 communicates with the air inlet 21 and the cylinder inner cavity 22. A first one-way conduction structure 31 is provided in the air intake passage 30, and the conduction direction of the first one-way conduction structure 31 is from the air inlet 21 to the cylinder inner cavity 22.

[0049] By using the cylinder 10 for a compressor provided in the embodiment of the present disclosure, an air intake passage 30 communicating with the air inlet 21 and the cylinder inner cavity 22 is provided in the cylinder block 20, so that the air inlet 21 does not directly communicate with the cylinder inner cavity 22. The air intake passage 30 can store the reversely flowing intake air flow and prevent the intake air flow from flowing back from the cylinder inner cavity 22 to the air inlet 21. A first one-way conduction structure 31 is provided in the air intake passage 30, allowing the intake air flow to flow forward from the air inlet 21 towards the cylinder inner cavity 22 and being able to prevent the intake air flow from flowing reversely from the cylinder inner cavity 22 towards the air inlet 21. By providing the air intake passage 30 between the air inlet 21 and the cylinder inner cavity 22 and providing the first one-way conduction structure 31 in the air intake passage 30, it is possible to effectively prevent the intake air flow from flowing back from the cylinder inner cavity 22 to the air inlet 21. This can keep the intake pulsation in a relatively stable state, avoid affecting the intake air volume of the compressor, and thus improve the compressor capacity.

[0050] Optionally, in combination Figures 1-3 As shown, the first one-way conduction structure 31 includes a first Tesla valve passage 32. The first Tesla valve passage 32 includes a first main passage 33 and a first branch passage 34. The first main passage 33 is arranged along the extending direction of the air intake passage 30 to communicate the air inlet 21 with the cylinder inner cavity 22. The first branch passage 34 is curved in an arc shape, and both ends of the first branch passage 34 communicate with the side wall of the first main passage 33 to form a resistance passage. Among them, along the direction from the air inlet 21 towards the cylinder inner cavity 22, the intake air flow flows along the first main passage 33. Along the direction from the cylinder inner cavity 22 towards the air inlet 21, the intake air flow can flow into the first branch passage 34 to form a diversion, so as to prevent the intake air flow from flowing from the cylinder inner cavity 22 towards the air inlet 21.

[0051] The first one-way conduction structure 31 includes a first Tesla valve passage 32. The air intake passage 30 is set as a Tesla valve structure inside, and the first branch passage 34 is curved in an arc shape to form a resistance passage. By increasing the complexity of the return path to improve the ability to prevent return, the one-way control of the intake air flow can be realized.

[0052] According to the structural characteristics of the Tesla valve, when the intake air flow flows forward from the intake port 21 towards the inner cavity 22 of the cylinder, the intake air flow will not flow into the first branch channel 34, and the intake air flow flows along the first main channel 33 and can pass through smoothly. When the intake fluid flows reversely from the inner cavity 22 of the cylinder towards the intake port 21, the intake air flow can flow into the first branch channel 34 to form a diversion, and will be subject to a greater flow resistance from the arc-shaped curved channel. In this way, the reversely flowing intake air flow can be stored in the first Tesla valve channel 32, so that the intake air flow can be better prevented from flowing back to the intake port. In this way, the intake pulsation can be in a stable state, improving the performance and reliability of the compressor.

[0053] Optionally, as shown in Figure 3 along the direction from the intake port 21 towards the inner cavity 22 of the cylinder, the first main channel 33 extends in a straight line.

[0054] The first main channel 33 extending in a straight line enables the air flow to flow more directly and smoothly along the direction from the intake port 21 towards the inner cavity 22 of the cylinder.

[0055] It can be understood that along the direction from the intake port 21 towards the inner cavity 22 of the cylinder, the first main channel 33 can also extend in a bent shape with multiple straight segments, or can extend in a curved shape, and can also enable the air flow to flow smoothly along the direction from the intake port 21 towards the inner cavity 22 of the cylinder.

[0056] The first one-way conduction structure 31 can also adopt a one-way valve structure such as a check valve or a lift valve, and the valve flow direction is from the intake port 21 to the inner cavity 22 of the cylinder.

[0057] Optionally, as shown in Figure 3 the first Tesla valve channel 32 includes a plurality of first branch channels 34, and the plurality of first branch channels 34 are relatively arranged on both sides of the first main channel 33.

[0058] The plurality of first branch channels 34 can increase the resistance to the intake air flow and improve the anti-backflow effect.

[0059] The plurality of first branch channels 34 are relatively arranged on both sides of the first main channel 33, which can increase the complexity of fluid flow. When the intake air flow flows reversely from the inner cavity 22 of the cylinder towards the intake port 21, the intake air flow can be effectively blocked from both sides of the first main channel 33 at the same time, enhancing the one-way flow effect of the first Tesla valve channel 32.

[0060] Optionally, the plurality of first branch channels 34 are symmetrically arranged on both sides of the first main channel 33.

[0061] A plurality of first branch channels 34 are symmetrically arranged on both sides of the first main channel 33, which can more effectively disperse the intake air flow and improve the effect of preventing the reverse flow of the intake air flow. The better the symmetry of the plurality of first branch channels 34, the better the unidirectional flow characteristic of the first Tesla valve channel 32.

[0062] It can be understood that the plurality of first branch channels 34 can also be partially symmetrically arranged or asymmetrically arranged on both sides of the first main channel 33.

[0063] Optionally, in combination with Figure 3 As shown, the first Tesla valve channel 32 includes a plurality of first branch channels 34, and the plurality of first branch channels 34 are arranged at intervals along the extension direction of the first main channel 33.

[0064] The plurality of first branch channels 34 are arranged at intervals along the extension direction of the first main channel 33, which can increase the path complexity of the reverse flow of the intake air flow. When the intake air flow fluid attempts to flow reversely along the inner cavity 22 of the cylinder towards the intake port 21, it needs to pass through the plurality of first branch channels 34, thereby increasing the flow resistance and enhancing the anti-backflow effect.

[0065] Optionally, the plurality of first branch channels 34 are oppositely arranged on both sides of the first main channel 33 and are arranged at intervals along the extension direction of the first main channel 33. This can effectively improve the anti-backflow performance of the first Tesla valve channel 32, thereby maintaining the efficient operation of the compressor.

[0066] Optionally, in combination with Figure 3 As shown, along the direction from the intake port 21 towards the inner cavity 22 of the cylinder, the first branch channel 34 extends in a hooked shape.

[0067] The hooked first branch channel 34 includes a relatively straight hook handle portion and a curved hook portion. The hook portion communicates with the position of the first main channel 33 close to the intake port 21 to form a hooked bend. When the intake air flow flows forward along the intake port 21 towards the inner cavity 22 of the cylinder, the hook portion can prevent the intake air flow from flowing into the first branch channel 34, so that the intake air flow flows smoothly along the first main channel 33. The hook handle portion communicates with the position of the first main channel 33 close to the inner cavity 22 of the cylinder and can guide the air flow into the first branch channel 34. When the intake air flow flows reversely along the inner cavity 22 of the cylinder towards the intake port 21, part of the intake air flow enters the first branch channel 34 through the right hook handle portion, flows through the hook portion and then converges into the first main channel 33, so that the reverse flow of the intake air flow is blocked.

[0068] Optionally, the ratio range between the volume of the first Tesla valve channel 32 and the cylinder displacement is greater than or equal to 0.02 and less than or equal to 0.1.

[0069] The volume of the first Tesla valve passage 32 is Vts, the cylinder displacement is Vc, and the ratio of the volume of the first Tesla valve passage 32 to the cylinder displacement is Vts / Vc, where 0.02 ≤ Vts / Vc ≤ 0.1.

[0070] When Vts / Vc is greater than or equal to 0.02, the first Tesla valve passage 32 can have a relatively large volume, so as to provide sufficient resistance space to prevent the backflow of the intake air flow. This can improve the one-way flow performance of the first Tesla valve passage 32, avoid or reduce the air flow pulsation caused by the backflow of the intake air flow, and reduce the impact on the intake air volume.

[0071] When Vts / Vc is less than or equal to 0.1, it can prevent a relatively large passage volume from occupying more space of the cylinder 10, improve the space utilization rate of the intake passage, and thus improve the operating efficiency of the compressor.

[0072] By setting the ratio of the volume of the first Tesla valve passage 32 to the cylinder displacement between 0.02 and 0.1, the first Tesla valve passage 32 can effectively play the role of preventing backflow without occupying too much space.

[0073] It can be understood that Vts / Vc can be 0.02, 0.04, 0.06, 0.08, 0.1.

[0074] Optionally, as shown in Figure 1 、 Figure 2 and Figure 7 , the intake passage 30 is arranged on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10.

[0075] The intake passage 30 is arranged on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10, which can simplify the structure of the cylinder 10 and facilitate production.

[0076] As shown in Figure 1 、 Figure 2 、 Figure 5 and Figure 7 , the intake passage 30 can be arranged on the upper end face 231 of the cylinder block 20 along the axial direction of the cylinder 10, or can be arranged on the lower end face 232 of the cylinder block 20 along the axial direction of the cylinder 10.

[0077] Optionally, as shown in Figure 2 and Figure 5 , the number of the intake passages 30 is multiple. The multiple intake passages 30 include a first intake passage 301 and a second intake passage 302. The first intake passage 301 is arranged on the upper end face 231 of the cylinder block 20 along the axial direction of the cylinder 10, and the second intake passage 302 is arranged on the lower end face 232 of the cylinder block 20 along the axial direction of the cylinder 10. Both the first intake passage 301 and the second intake passage 302 are communicated with the intake port 21 and the inner cavity 22 of the cylinder.

[0078] The first suction channel 301 and the second suction channel 302 provided on the upper end face 231 and the lower end face 232 of the cylinder block 20 along the axial direction of the cylinder 10 are used to convey the suction air flow, which can improve the suction efficiency. At the same time, a first one-way conduction structure 31 is provided in both the first suction channel 301 and the second suction channel 302, which can prevent the suction air flow from flowing back.

[0079] Optionally, in combination Figures 1-3 and Figure 5 As shown in the figure, an inhalation bevel cut 24 is provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10. The inhalation bevel cut 24 communicates with the suction channel 30 and the inner cavity 22 of the cylinder block to guide the suction air flow from the suction channel 30 to the inner cavity 22 of the cylinder block; wherein, along the direction of the suction channel 30 towards the inner cavity 22 of the cylinder block, the diameter of the inhalation bevel cut 24 gradually increases.

[0080] The inhalation bevel cut 24 is provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10, making the transition from the suction channel 30 to the inner cavity 22 of the cylinder block smoother. As the inhalation bevel cut 24 extends in the direction from the suction channel 30 towards the inner cavity 22 of the cylinder block, its diameter gradually increases, which can reduce the resistance and turbulence of the air flow, thereby improving the suction efficiency. The setting of the inhalation bevel cut 24 reduces energy loss and improves the performance of the compressor.

[0081] The inhalation bevel cut 24 can be provided on the upper end face 231 of the cylinder block 20 along the axial direction of the cylinder 10, or can be provided on the lower end face 232 of the cylinder block 20 along the axial direction of the cylinder 10.

[0082] Optionally, in combination Figure 2 and Figure 5 As shown in the figure, the number of inhalation bevel cuts 24 is multiple, and the multiple inhalation bevel cuts 24 include a first inhalation bevel cut 242 and a second inhalation bevel cut 243; the number of suction channels 30 is multiple, and the multiple suction channels 30 include a first suction channel 301 and a second suction channel 302; wherein, the first inhalation bevel cut 242 and the first suction channel 301 are provided on the upper end face 231 of the cylinder block 20 along the axial direction of the cylinder 10, and the first inhalation bevel cut 242 communicates with the first suction channel 301 and the inner cavity 22 of the cylinder block; the second inhalation bevel cut 243 and the second suction channel 302 are provided on the lower end face 232 of the cylinder block 20 along the axial direction of the cylinder 10, and the second inhalation bevel cut 243 communicates with the second suction channel 302 and the inner cavity 22 of the cylinder block.

[0083] Providing a first inhalation bevel cut 242 between the first suction channel 301 on the upper end face 231 of the cylinder 10 and the inner cavity 22 of the cylinder block, and providing a second inhalation bevel cut 243 between the second suction channel 302 on the lower end face 232 of the cylinder 10 and the inner cavity 22 of the cylinder block can more effectively improve the suction efficiency.

[0084] Optionally, the cylinder block 20 is further provided with a sliding vane groove 25. Along the circumferential direction of the cylinder 10, the angle range between the center line 241 of the suction inclined notch and the center line 251 of the sliding vane groove is greater than or equal to 5° and less than or equal to 23°.

[0085] The angle between the center line 241 of the suction inclined notch and the center line 251 of the sliding vane groove is as Figure 6 shown as α in, 5° ≤ α ≤ 23°.

[0086] The angle α between the center line 241 of the suction inclined notch and the center line 251 of the sliding vane groove is the suction angle. Generally, the larger the displacement of the cylinder 10, the larger the suction angle.

[0087] When α is greater than or equal to 5°, it can avoid too small a suction angle and prevent the premature closing of the suction inclined notch 24 resulting in insufficient suction, thereby improving the suction efficiency.

[0088] When α is less than or equal to 23°, it can improve the air flow guiding efficiency, enabling the air flow to smoothly enter the inner cavity 22 of the cylinder block. At the same time, it can also reduce the flow resistance of the air flow and improve the suction efficiency.

[0089] The embodiment of the present disclosure defines 5° ≤ α ≤ 23°, which can increase the suction volume while reducing the flow resistance of the suction air flow, thereby effectively improving the suction efficiency.

[0090] It can be understood that α can be 5°, 10°, 15°, 20°, 23°.

[0091] Optionally, as shown in combination with Figure 1 , Figure 2 and Figure 4 , the cylinder block 20 is further provided with an exhaust passage 40 and an exhaust port 26. The exhaust passage 40 communicates the inner cavity 22 of the cylinder block and the exhaust port 26. The exhaust passage 40 is provided with a second one-way valve structure 41, and the conduction direction of the second one-way valve structure 41 is from the inner cavity 22 of the cylinder block to the exhaust port 26.

[0092] An exhaust passage 40 is provided between the exhaust port 26 and the cylinder inner cavity 22, such that the cylinder inner cavity 22 is not directly connected to the exhaust port 26. The exhaust passage 40 can store the reversely flowing exhaust gas flow and prevent the exhaust gas flow from flowing back from the exhaust port 26 to the cylinder inner cavity 22. A second one-way valve structure 41 is provided in the exhaust passage 40 to control the one-way flow of the exhaust gas flow. The second one-way valve structure 41 allows the exhaust gas flow to flow forward from the cylinder inner cavity 22 towards the exhaust port 26 and can prevent the exhaust gas flow from flowing reversely from the exhaust port 26 towards the cylinder inner cavity 22. Through the arrangement of the exhaust passage 40 and the second one-way valve structure 41, the one-way fluidity of the exhaust gas flow can be improved, and the exhaust gas flow can be prevented from flowing back from the exhaust port 26 to the cylinder inner cavity 22. This can keep the exhaust pulsation in a relatively stable state, avoid affecting the exhaust volume of the compressor, and thus improve the compressor capacity.

[0093] Optionally, as shown in combination with Figure 1 、 Figure 2 and Figure 4 The second one-way valve structure 41 includes a second Tesla valve passage 42. The second Tesla valve passage 42 includes a second main passage 43 and a second branch passage 44. The second main passage 43 is arranged along the extending direction of the exhaust passage 40 to connect the cylinder inner cavity 22 and the exhaust port 26; the second branch passage 44 is curved in an arc shape, and both ends of the second branch passage 44 are connected to the side wall of the second main passage 43 to form a resistance passage; wherein, along the direction from the cylinder inner cavity 22 towards the exhaust port 26, the exhaust gas flow flows along the second main passage 43; along the direction from the exhaust port 26 towards the cylinder inner cavity 22, the exhaust gas flow can flow into the second branch passage 44 to form a diversion, so as to prevent the exhaust gas flow from flowing from the exhaust port 26 towards the cylinder inner cavity 22.

[0094] As shown in combination with Figure 1 、 Figure 2 and Figure 4 By arranging the second Tesla valve passage 42 in the exhaust passage 40, the exhaust gas flow can be smoothly guided from the cylinder inner cavity 22 to the exhaust port 26, and the curved second branch passage 44 can prevent the exhaust gas flow from flowing from the exhaust port 26 to the cylinder inner cavity 22. The second Tesla valve passage 42 can effectively prevent the exhaust gas flow from flowing back, reduce energy waste, and thus improve the energy efficiency of the compressor.

[0095] The second Tesla valve passage 42 adopts the same or similar structural design as the first Tesla valve passage 32.

[0096] Optionally, as shown in combination with Figure 4 The second Tesla valve passage 42 includes a plurality of second branch passages 44, and the plurality of second branch passages 44 are oppositely arranged on both sides of the second main passage 43.

[0097] Multiple second branch channels 44 can increase the resistance to the exhaust gas flow and enhance the anti-backflow effect.

[0098] Multiple second branch channels 44 are oppositely arranged on both sides of the second main channel 43, which can increase the complexity of fluid flow. When the exhaust gas flow reversely flows along the exhaust port 26 towards the cylinder inner cavity 22, it can effectively block the exhaust gas flow from both sides of the second main channel 43 simultaneously, enhancing the one-way flow effect of the second Tesla valve channel 42.

[0099] Optionally, multiple second branch channels 44 are symmetrically arranged on both sides of the second main channel 43.

[0100] Multiple second branch channels 44 are symmetrically arranged on both sides of the second main channel 43, which can more effectively disperse the exhaust gas flow and improve the effect of blocking the reverse flow of the exhaust gas flow. The better the symmetry of the multiple second branch channels 44, the better the one-way flow characteristics of the second Tesla valve channel 42.

[0101] It can be understood that multiple second branch channels 44 can also be partially symmetrically arranged or asymmetrically arranged on both sides of the second main channel 43.

[0102] Optionally, as shown in combination Figure 4 The second Tesla valve channel 42 includes multiple second branch channels 44, and the multiple second branch channels 44 are arranged at intervals along the extension direction of the second main channel 43.

[0103] The multiple second branch channels 44 are arranged at intervals along the extension direction of the second main channel 43, which can increase the path complexity of the reverse flow of the exhaust gas flow. When the exhaust gas flow fluid attempts to reversely flow along the exhaust port 26 towards the cylinder inner cavity 22, it needs to pass through the multiple second branch channels 44, thereby increasing the flow resistance and enhancing the anti-backflow effect.

[0104] Optionally, multiple second branch channels 44 are oppositely arranged on both sides of the second main channel 43 and are arranged at intervals along the extension direction of the second main channel 43. This can effectively improve the anti-backflow performance of the second Tesla valve channel 42, thereby maintaining the efficient operation of the compressor.

[0105] Optionally, the ratio range of the volume of the second Tesla valve channel 42 to the cylinder displacement is greater than or equal to 0.01 and less than or equal to 0.02.

[0106] The volume of the second Tesla valve channel 42 is Vtd, the cylinder displacement is Vc, and 0.01 ≤ Vtd / Vc ≤ 0.02.

[0107] When Vtd / Vc is greater than or equal to 0.01, it can provide sufficient resistance space to effectively prevent the reverse flow of the exhaust gas flow, improve the one-way control effect of the second Tesla valve channel 42, and improve the exhaust efficiency. At the same time, it can also effectively prevent the gas from being repeatedly compressed in the cylinder inner cavity 22, avoid the increase of the compressor input power, and improve the energy efficiency of the compressor.

[0108] When Vtd / Vc is less than or equal to 0.02, it can avoid the excessive volume of the second Tesla valve channel 42, reduce the pressure loss of the exhaust gas flow, and reduce the power consumption of the compressor.

[0109] By setting the ratio of the volume of the second Tesla valve channel 42 to the displacement of the cylinder 10 between 0.01 and 0.02 in the embodiments of the present disclosure, the effectiveness of the one-way flow control of the exhaust gas flow by the second Tesla valve channel 42 can be improved, and at the same time, the pressure loss of the exhaust gas flow can be reduced.

[0110] It can be understood that Vtd / Vc can be 0.01, 0.012, 0.015, 0.018, 0.02.

[0111] Optionally, in combination with Figure 1 , Figure 2 and Figure 7 as shown, the exhaust passage 40 and the exhaust port 26 are both provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10.

[0112] The exhaust passage 40 and the exhaust port 26 are provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10, which can simplify the structure of the cylinder 10 and facilitate production.

[0113] The exhaust passage 40 and the exhaust port 26 can be provided on the upper end face 231 of the cylinder block 20 along the axial direction of the cylinder 10, or can be provided on the lower end face 232 of the cylinder block 20 along the axial direction of the cylinder 10.

[0114] Optionally, in combination with Figure 1 , Figure 2 , Figure 4 and Figure 6 as shown, an exhaust bevel cut 27 is provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10, and the exhaust bevel cut 27 communicates the cylinder inner cavity 22 and the exhaust passage 40 to guide the exhaust gas flow from the cylinder inner cavity 22 to the exhaust passage 40; wherein, along the direction from the cylinder inner cavity 22 towards the exhaust passage 40, the diameter of the exhaust bevel cut 27 gradually decreases.

[0115] An exhaust inclined cut 27 is provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10, which can make the transition from the inner cavity 22 of the cylinder block to the exhaust passage 40 smoother. The diameter of the exhaust inclined cut 27 gradually decreases in the direction from the inner cavity 22 of the cylinder block towards the exhaust passage 40, reducing the speed of the exhaust gas flow accordingly, and being able to reduce the kinetic energy loss during the exhaust process. At the same time, it can also reduce the turbulence and noise generated by the exhaust gas flow during the discharge process, improving the running stability of the system.

[0116] Optionally, as shown in combination with Figure 6 shown, the cylinder block 20 is further provided with a sliding vane groove 25. Along the circumferential direction of the cylinder 10, the angle range between the center line 271 of the exhaust inclined cut and the center line 251 of the sliding vane groove is greater than or equal to 5° and less than or equal to 15°.

[0117] The angle between the center line 271 of the exhaust inclined cut and the center line 251 of the sliding vane groove is as shown by β in Figure 6 the figure, 5° ≤ β ≤ 15°. The angle β between the center line 271 of the exhaust inclined cut and the center line 251 of the sliding vane groove is the exhaust angle. Generally, the larger the displacement of the cylinder 10, the larger the exhaust angle.

[0118] When β is greater than or equal to 5°, enough space can be reserved to set the exhaust flow channel, enabling the compressed gas to be discharged smoothly. β being greater than or equal to 5° can also improve the exhaust efficiency, enabling the compressed gas to be discharged quickly and avoiding retention in the inner cavity 22 of the cylinder block.

[0119] When β is less than or equal to 15°, the volumetric efficiency of the cylinder 10 can be improved, the energy loss during the exhaust process can be reduced, and the energy efficiency of the compressor can be improved. At the same time, a compact design of the cylinder 10 can also be achieved.

[0120] In the embodiments of the present disclosure, it is defined that 5° ≤ β ≤ 15°, which can improve the exhaust sufficiency, avoid large fluctuations in the suction pulsation caused by untimely exhaust, and at the same time, can also reduce the pressure loss and improve the energy efficiency of the compressor.

[0121] It can be understood that β can be 5°, 8°, 10°, 12°, 15°.

[0122] The embodiments of the present disclosure provide a compressor, characterized in that it includes a cylinder 10 for a compressor as described in any one of the above - mentioned embodiments.

[0123] The compressor provided by the embodiments of the present disclosure, because it includes a cylinder 10 for a compressor as described in any one of the above - mentioned embodiments, thus has all the beneficial effects of the cylinder 10 for a compressor as described in any one of the above - mentioned embodiments. Through the arrangement of the suction channel 30 and the first one - way conduction structure 31, the suction efficiency of the compressor can be improved, the backflow of the suction air flow can be reduced, and the energy efficiency of the compressor can be improved.

[0124] Optionally, in combination with Figure 7 As shown, the compressor includes a pump body assembly 60, and the pump body assembly 60 includes a cylinder 10 and a bearing 50. When the suction passage 30 is provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10 and / or the exhaust passage 40 is provided on the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10, the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10 is in contact with the surface of the bearing 50.

[0125] The fact that the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10 is in contact with the surface of the bearing 50 can form a sealed suction passage 30 between the end face of the cylinder block 20 and the surface of the bearing 50, improving the suction effect. The fact that the end face 23 of the cylinder block 20 along the axial direction of the cylinder 10 is in contact with the surface of the bearing 50 can form a sealed exhaust passage 40 between the end face of the cylinder block 20 and the surface of the bearing 50, improving the exhaust effect.

[0126] Optionally, in combination with Figure 7 As shown, the bearing 50 includes a main bearing 51 and a sub-bearing 52. The surface of the main bearing 51 can be in contact with the upper end face 231 of the cylinder block 10 along the axial direction of the cylinder 10, and the surface of the sub-bearing 52 can be in contact with the lower end face 232 of the cylinder block 10 along the axial direction of the cylinder 10.

[0127] When the suction passage 30 or the exhaust passage 40 is provided on the upper end face 231 along the axial direction of the cylinder 10, a sealed suction passage 30 or exhaust passage 40 can be formed between the surface of the main bearing 51 and the upper end face 231. When the suction passage 30 or the exhaust passage 40 is provided on the lower end face 232 along the axial direction of the cylinder 10, a sealed suction passage 30 or exhaust passage 40 can be formed between the surface of the sub-bearing 52 and the lower end face 232. This can improve the suction or exhaust effect.

[0128] The above description and the drawings fully illustrate the embodiments of the present disclosure so that those skilled in the art can practice them. Other embodiments may include structural and other changes. The embodiments only represent possible variations. Unless explicitly required, the individual components and functions are optional, and the order of operations can vary. Parts and features of some embodiments can be included in or replaced by parts and features of other embodiments. The embodiments of the present disclosure are not limited to the structures already described and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present disclosure is only limited by the appended claims.

Claims

1. A cylinder for a compressor, characterized in that: include: The cylinder body is provided with an air intake port, an air intake passage and a cylinder inner cavity, wherein the air intake passage connects the air intake port and the cylinder inner cavity; The first one-way conducting structure is arranged in the air intake passage, and the conducting direction of the first one-way conducting structure is from the air intake port to the inner cavity of the cylinder body.

2. The cylinder for a compressor according to claim 1, characterized in that: The first unidirectional conduction structure includes a first Tesla valve channel, and the first Tesla valve channel includes: A first main flow channel is arranged along the extension direction of the air intake channel to connect the air intake port with the inner cavity of the cylinder body; The first branch channel is curved in an arc shape, and both ends of the first branch channel are connected to the side wall of the first main channel to form a resistance channel; Among them, along the direction of the air intake port toward the inner cavity of the cylinder body, the air intake air flows along the first mainstream channel; along the direction of the inner cavity of the cylinder body toward the air intake port, the air intake air can flow into the first branch channel to form a diversion to prevent the air intake air from flowing from the inner cavity of the cylinder body toward the air intake port.

3. The cylinder for a compressor according to claim 2, characterized in that: The first Tesla valve channel includes a plurality of first branch channels, and the plurality of first branch channels are relatively arranged on two sides of the first main channel; and / or, The first Tesla valve channel includes a plurality of first branch channels, and the plurality of first branch channels are arranged at intervals along an extension direction of the first main channel.

4. The cylinder for a compressor according to claim 2, characterized in that: The ratio of the volume of the first Tesla valve passage to the cylinder displacement is in the range of greater than or equal to 0.02 and less than or equal to 0.

1.

5. The cylinder for a compressor according to claim 1, characterized in that: An air intake bevel cutout is provided on the end surface of the cylinder body along the axial direction of the cylinder, and the air intake bevel cutout connects the air intake passage and the inner cavity of the cylinder body to guide the air intake flow from the air intake passage to the inner cavity of the cylinder body; Wherein, along the direction of the air intake passage toward the inner cavity of the cylinder body, the diameter of the air intake oblique cut gradually increases.

6. The cylinder for a compressor according to claim 5, characterized in that: The cylinder body is also provided with a vane groove. Along the circumference of the cylinder, the angle between the center line of the suction oblique cut and the center line of the vane groove is greater than or equal to 5° and less than or equal to 23°.

7. The cylinder for a compressor according to any one of claims 1 to 6, characterized in that: The cylinder body is also provided with an exhaust passage and an exhaust port. The exhaust passage connects the inner cavity of the cylinder body and the exhaust port. The exhaust passage is provided with a second one-way valve structure. The conduction direction of the second one-way valve structure is from the inner cavity of the cylinder body to the exhaust port.

8. The cylinder for a compressor according to claim 7, characterized in that: The second one-way valve structure includes a second Tesla valve channel, and the second Tesla valve channel includes: A second main flow channel is provided along the extension direction of the exhaust channel to connect the inner cavity of the cylinder body with the exhaust port; The second branch channel is curved in an arc shape, and both ends of the second branch channel are connected to the side wall of the second main channel to form a resistance channel; Among them, the exhaust airflow flows along the second mainstream channel along the direction from the cylinder inner cavity toward the exhaust port; along the direction from the exhaust port toward the cylinder inner cavity, the exhaust airflow can flow into the second branch channel to form a diversion to prevent the exhaust airflow from flowing from the exhaust port toward the cylinder inner cavity.

9. The cylinder for a compressor according to claim 8, characterized in that: The ratio of the volume of the second Tesla valve passage to the cylinder displacement is in the range of greater than or equal to 0.01 and less than or equal to 0.

02.

10. The cylinder for a compressor according to claim 7, characterized in that: An exhaust bevel cutout is provided on the end surface of the cylinder body along the axial direction of the cylinder, and the exhaust bevel cutout connects the inner cavity of the cylinder body and the exhaust passage to guide the exhaust airflow from the inner cavity of the cylinder body to the exhaust passage; Wherein, along the direction from the inner cavity of the cylinder body toward the exhaust passage, the diameter of the exhaust oblique cut gradually decreases.

11. The cylinder for a compressor according to claim 10, characterized in that: The cylinder body is also provided with a vane groove, and along the circumference of the cylinder, the angle range between the center line of the exhaust oblique cut and the center line of the vane groove is greater than or equal to 5° and less than or equal to 15°.

12. A compressor, characterized in that: The invention comprises a cylinder for a compressor according to any one of claims 1 to 11.

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