Air cylinder and rotor type compressor

Abstract

The utility model relates to the technical field of compressors, and particularly discloses a cylinder and a rotor type compressor, an exhaust structure comprises a plurality of diversion trenches and a plurality of exhaust ports, the diversion trenches and the exhaust ports are arranged on the inner wall of a cylinder body, the diversion trenches are communicated with the exhaust ports, the diversion trenches are closer to a slip sheet groove than the exhaust ports, the number of the diversion trenches is n, the displacement of the cylinder body is V, the width of the flow guide groove is D, the length of the flow guide groove is L, the depth of the flow guide groove is H, and D, L, H, n and V meet the formula of D * L * H * nlt, v / 100. The flow guide groove is formed in the inner wall of the cylinder body, a connecting channel between overcompressed gas and the exhaust port is established, the overcompressed gas can be better exhausted, the situation that the compressor is influenced by reexpansion of the part of high-pressure gas is avoided, and meanwhile the size of the flow guide groove is set, so that the size of the flow guide groove is smaller than one percent of the gas displacement. The problem that the compression ratio of a compressor system is reduced due to the fact that the clearance volume of a flow guide groove is too large is solved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a cylinder and rotor type compressor. Background Art

[0002] The rotary compressor includes a shell, a motor assembly and a pump body section are accommodated inside the shell, and the pump body section includes an upper cylinder head, at least one cylinder and a lower cylinder head, etc. The rotary compressor works by using the rotational driving force of the motor. When the cylinder is exhausting, the exhaust hole in the cylinder and the blade groove are set at a certain angle, so that a sealing area (over-compression area) is generated between the cylinder and the blades in each rotation cycle of the piston. The gas in the sealing area cannot be discharged in time, and will be continuously compressed with the rotation of the crankshaft, the pressure will continue to increase, and a sudden increase in force will be generated in the radial direction of the crankshaft, so that the indicated work of the compressor increases, and the instability of the compressor system is further increased. In particular, the demand for large-displacement compressors is gradually increasing, and the side exhaust angle is much increased compared to the traditional exhaust angle, which causes the volume of the over-compression area to increase, and the influence of the over-compressed gas on the compressor system will be further enhanced. Utility Model Content

[0003] The utility model aims to provide a cylinder and a rotor type compressor to solve the over-compression problem of the existing rotor type compressor during the exhaust process.

[0004] In order to achieve the above purpose, the utility model adopts the following technical solutions:

[0005] In one aspect, the utility model provides a cylinder, comprising:

[0006] A cylinder body, wherein a sliding plate groove is provided on the cylinder body;

[0007] An exhaust structure, wherein the exhaust structure includes a plurality of guide grooves and a plurality of exhaust ports, wherein the guide grooves and the exhaust ports are both opened on the inner wall of the cylinder body, the guide grooves are connected to the exhaust ports, and the guide grooves are closer to the slide grooves than the exhaust ports, the number of the guide grooves is n, the displacement of the cylinder body is V, the width of the guide groove is D, the length of the guide groove is L, the depth of the guide groove is H, and D, L, H, n and V satisfy: D*L*H*n <V / 100。

[0008] As a preferred technical solution of the above-mentioned cylinder, each of the exhaust ports is connected to one or more of the guide grooves; or, multiple exhaust ports are connected to one guide groove.

[0009] As a preferred technical solution of the above cylinder, the number of the exhaust ports is m, the depth of the exhaust ports is T, and the radius of the exhaust ports is R, wherein D, L, H, n, R, T and m satisfy: D*L*H*n<π*R 2 *T*m / 100.

[0010] As a preferred technical solution of the above-mentioned cylinder, T and H satisfy: 4H<T.

[0011] As a preferred technical solution of the above-mentioned cylinder, the diameter of the exhaust port is B, and B and D satisfy: D≤B.

[0012] As a preferred technical solution of the above-mentioned cylinder, the depth of the guide groove ranges from 0.1 mm to 4 mm.

[0013] As a preferred technical solution of the above-mentioned cylinder, a plurality of the exhaust ports are connected to one guide groove.

[0014] On the other hand, the utility model also provides a rotor compressor, including a crankshaft, a piston, blades, and the cylinder described in any of the above schemes, wherein the blades are slidably arranged in the vane grooves and abut against the piston, the crankshaft is transmission-connected to the piston and can drive the piston to be rollingly arranged in the cylinder body, the axis of the exhaust port is arranged at an angle to the axis of the vane groove, the piston, the inner wall of the cylinder body and the blades can surround and form an over-compression cavity, and the guide groove connects the over-compression cavity and the exhaust port.

[0015] As a preferred technical solution of the above-mentioned rotary compressor, the volume of the over-compression cavity is W, and D, L, H, n and W satisfy: L*D*H*n≤W.

[0016] As a preferred technical solution of the above-mentioned rotary compressor, L*D*H*n≤W / 2.

[0017] The beneficial effects of the utility model are:

[0018] The present utility model provides a cylinder and a rotary compressor. The cylinder includes a cylinder block and an exhaust structure. A sliding vane groove is provided on the cylinder block. The exhaust structure includes a plurality of flow guiding grooves and a plurality of exhaust ports. Both the flow guiding grooves and the exhaust ports are formed on the inner wall of the cylinder block. The flow guiding grooves are communicated with the exhaust ports, and the flow guiding grooves are closer to the sliding vane groove than the exhaust ports. The number of the flow guiding grooves is n, the displacement of the cylinder block is V, the width of the flow guiding groove is D, the length of the flow guiding groove is L, the depth of the flow guiding groove is H, and D, L, H, n and V satisfy: D * L * H * n < V / 100. By providing the flow guiding grooves on the inner wall surface of the cylinder block and making the flow guiding grooves closer to the sliding vane groove, a connection channel between the over-compressed gas and the exhaust port is established, which is more conducive to timely discharging the over-compressed gas generated during the exhaust process, so as to avoid the impact on the compressor caused by the re-expansion of this part of high-pressure gas, and improve the overall stability and reliability of the compressor system. At the same time, by setting the size of the flow guiding grooves, the volume thereof is made less than one percent of the exhaust volume, so as to further solve the problem that the compression ratio of the compressor system is reduced due to the too large clearance volume of the flow guiding grooves. Description of the Drawings

[0019] Figure 1 Structural schematic diagram of the cylinder provided by the present utility model Figure 1 ;

[0020] Figure 2 Structural schematic diagram of the cylinder provided by the present utility model Figure 2 ;

[0021] Figure 3 is Figure 2 partial enlarged view of part E in

[0022] Figure 4 Structural schematic diagram of the cylinder provided by the present utility model Figure 3 ;

[0023] Figure 5 Structural schematic diagram of the cylinder provided by the present utility model Figure 4 ;

[0024] Figure 6 Structural schematic diagram of the cylinder provided by the present utility model Figure 5 ;

[0025] Figure 7 Structural schematic diagram of the cylinder provided by the present utility model Figure 6 .

[0026] Wherein:

[0027] 1, cylinder block; 2, sliding vane groove; 3, flow guiding groove; 4, exhaust port. Detailed Embodiment

[0028] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and should not be construed as limiting the present invention.

[0029] In the description of the present invention, it should be noted that the terms "center", "up", "down", "left", "right", "vertical", "horizontal", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance. Among them, the terms "first position" and "second position" are two different positions.

[0030] Unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in this utility model can be understood according to specific circumstances.

[0031] Unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include the first feature being in direct contact with the second feature, or may include the first feature being in contact with the second feature through another feature between them instead of being in direct contact. Moreover, a first feature being "above", "above" and "above" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes the first feature being directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0032] The technical solution of the utility model is further explained below with reference to the accompanying drawings and through specific implementation methods.

[0033] like Figures 1 to 7As shown in the figure, this embodiment provides a cylinder, which includes a cylinder block 1 and an exhaust structure. A sliding vane groove 2 is provided on the cylinder block 1. The exhaust structure is connected to an exhaust valve (not shown in the figure). The exhaust structure includes a plurality of flow guiding grooves 3 and a plurality of exhaust ports 4. Both the flow guiding grooves 3 and the exhaust ports 4 are formed on the inner wall of the cylinder block 1. The flow guiding grooves 3 are connected to the exhaust ports 4, and the flow guiding grooves 3 are closer to the sliding vane groove 2 than the exhaust ports 4. The number of the flow guiding grooves 3 is n, the displacement of the cylinder block 1 is V, the width of the flow guiding groove 3 is D, the length of the flow guiding groove 3 is L, the depth of the flow guiding groove 3 is H, and D, L, H, n, and V satisfy: D * L * H * n < V / 100. With such a setting, by forming the flow guiding grooves 3 on the inner wall surface of the cylinder block 1 and making the flow guiding grooves 3 approach the sliding vane groove 2, a connection channel between the over-compressed gas and the exhaust port 4 is established, which is more conducive to timely discharging the over-compressed gas generated during the exhaust process, so as to avoid the impact on the compressor caused by the re-expansion of this part of high-pressure gas, and improve the overall stability and reliability of the compressor system. It should be noted that the flow guiding grooves 3 are connected to the exhaust ports 4 but not to the sliding vane groove 2.

[0034] Optionally, each exhaust port 4 is correspondingly connected to one or more flow guiding grooves 3; or, a plurality of exhaust ports 4 are connected to one flow guiding groove 3. Further, a plurality of exhaust ports 4 are connected to one flow guiding groove 3. With such a setting, by providing one or more flow guiding grooves 3, the pressure of the over-compressed gas is reduced, and the influence of the over-compressed gas on the performance of the compressor and the force on the crankshaft shafting is reduced.

[0035] Specifically, please refer to Figures 5 to 7 , in this embodiment, the following solutions are exemplarily given: the number of the exhaust ports 4 is two, the number of the flow guiding grooves 3 is two, and the two flow guiding grooves 3 are correspondingly connected to the two exhaust ports 4 one by one; or, the number of the exhaust ports 4 is two, and each exhaust port 4 is connected to two flow guiding grooves 3; or, the number of the flow guiding grooves 3 is one, the number of the exhaust ports 4 is two, and one flow guiding groove 3 is simultaneously connected to the two exhaust ports 4.

[0036] Optionally, the number of the exhaust ports 4 is m, the depth of the exhaust port 4 is T, and the radius of the exhaust port 4 is R, where D, L, H, n, R, T, and m satisfy: D * L * H * n < π * R 2 * T * m / 100. In this way, it can be ensured that while the over-compressed gas is discharged in time, the problem of excessive clearance volume leading to a reduction in the compression ratio of the compressor system, a decrease in the compressor efficiency, and an increase in energy consumption is prevented.

[0037] Further, where T and H satisfy: 4H < T, to prevent excessive clearance volume.

[0038] Optionally, the diameter of the exhaust port 4 is B, and B and D satisfy: D≤B. By limiting the width of the guide groove to be below the diameter of the exhaust port, the gas reflowing in the guide groove can be further effectively compressed, thereby improving the compression efficiency.

[0039] Optionally, the depth of the guide groove 3 is between 0.1 mm and 4 mm. Exemplarily, the depth of the guide groove 3 can be 0.1 mm, 0.88 mm, 1.66 mm, 2.44 mm, 3.22 mm or 4 mm. By limiting the depth of the guide groove 3, it is prevented that the guide groove is too deep to increase the deformation of the wall near the exhaust port, thereby ensuring its structural strength and reliability, and at the same time ensuring the airtightness of the exhaust valve.

[0040] The present embodiment also provides a rotor compressor, comprising a crankshaft, a piston, blades, and the cylinder in the above scheme, wherein the blades are slidably arranged in the vane groove 2 and abut against the piston, the crankshaft is transmission-connected to the piston and can drive the piston to roll in the cylinder body 1, the axis of the exhaust port 4 is arranged at an angle to the axis of the vane groove 2, the piston, the inner wall of the cylinder body 1 and the blades can surround and form a compression cavity, and the guide groove 3 connects the compression cavity and the exhaust port 4.

[0041] It should be noted that half of the inner diameter of the cylinder 1 is K1, the radius of the piston is K2, the height of the cylinder 1 is E, and the displacement of the cylinder 1 is V = π*(K1 2 -K2 2 )*E.

[0042] Optionally, the volume of the over-compression cavity is W, and D, L, H, n and W satisfy: L*D*H*n≤W. This ensures that the reflux gas in the guide groove is further effectively compressed, thereby improving the compression efficiency.

[0043] Optionally, L*D*H*n≤W / 2, which can further improve the compression effect and reduce the occurrence of insufficient compression.

[0044] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation methods of the present invention. For those skilled in the art, other different forms of changes or modifications can be made based on the above description. It is not necessary and impossible to list all implementation methods here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the claims of the present invention.

Claims

1. A cylinder, characterized in that: include: A cylinder body (1), wherein the cylinder body (1) is provided with a sliding vane groove (2); An exhaust structure, wherein the exhaust structure comprises a plurality of guide grooves (3) and a plurality of exhaust ports (4), wherein the guide grooves (3) and the exhaust ports (4) are both opened on the inner wall of the cylinder body (1), the guide grooves (3) are connected to the exhaust ports (4), and the guide grooves (3) are closer to the vane grooves (2) than the exhaust ports (4), the number of the guide grooves (3) is n, the displacement of the cylinder body (1) is V, the width of the guide grooves (3) is D, the length of the guide grooves (3) is L, the depth of the guide grooves (3) is H, and D, L, H, n and V satisfy: D*L*H*n <V / 100。 2. The cylinder according to claim 1, characterized in that Each of the exhaust ports (4) is connected to one or more guide grooves (3); or, a plurality of the exhaust ports (4) are connected to one guide groove (3).

3. The cylinder according to claim 1, characterized in that The number of the exhaust ports (4) is m, the depth of the exhaust ports (4) is T, and the radius of the exhaust ports (4) is R, wherein D, L, H, n, R, T and m satisfy: D*L*H*n<π*R 2 *T*m / 100.

4. The cylinder according to claim 3, characterized in that in, T and H satisfy: 4H<T.

5. The cylinder according to claim 1, characterized in that The diameter of the exhaust port (4) is B, and B and D satisfy: D≤B.

6. The cylinder according to claim 1, characterized in that The depth of the guide groove (3) is between 0.1 mm and 4 mm.

7. The cylinder according to claim 2, characterized in that The plurality of exhaust ports (4) are connected to one guide groove (3).

8. A rotary compressor, characterized in that: The invention comprises a crankshaft, a piston, a blade, and a cylinder as claimed in any one of claims 1 to 7, wherein the blade is slidably arranged in the vane groove (2) and abuts against the piston, the crankshaft is transmission-connected to the piston and can drive the piston to be rollingly arranged in the cylinder body (1), the axis of the exhaust port (4) is arranged at an angle to the axis of the vane groove (2), the piston, the inner wall of the cylinder body (1) and the blade can surround and form an over-compression cavity, and the guide groove (3) connects the over-compression cavity and the exhaust port (4).

9. The rotary compressor according to claim 8, characterized in that: The volume of the over-compression cavity is W, and D, L, H, n and W satisfy: L*D*H*n≤W.

10. The rotary compressor according to claim 9, characterized in that: L*D*H*n≤W / 2.

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