Air cylinder with air supply structure and compressor

Abstract

The invention relates to the field of compressors, particularly provides an air cylinder with an air supplementing structure and a compressor, and aims to solve the problem that the air supplementing effect of an air supplementing structure of an existing compressor is poor. In order to achieve the purpose, the air cylinder with the air supplementing structure comprises an air cylinder body, a mounting groove is formed in the air cylinder body, an axial air supplementing channel is formed in the groove bottom of the mounting groove, a radial air supplementing channel and a communicating groove are further formed in the air cylinder body, and the two ends of the radial air supplementing channel communicate with an air supplementing device and the axial air supplementing channel correspondingly; the sectional area of the radial air supply channel is larger than that of the axial air supply channel; the valve cover is arranged in the mounting groove, a receding space is formed between the valve cover and the mounting groove, a circulating groove is formed in the valve cover, and the receding space communicates with the compression cavity through the circulating groove and the communicating groove; the gulp valve is arranged between the receding space and the axial gas supplementing channel in an openable and closable mode. By means of the air cylinder with the air supply structure, the air supply effect can be effectively improved, and the low-temperature heating performance is improved.

Description

Technical Field

[0001] This invention relates to the field of compressors, and specifically provides a cylinder and compressor with a gas replenishment structure. Background Technology

[0002] Conventional rotary compressors consist of a distributor, upper cover assembly, housing assembly, lower cover, pump body, motor, and refrigerant oil, and are used in heat pump heating systems. When the outdoor ambient temperature is below -15 degrees Celsius, the compressor's heating capacity is severely reduced because the refrigerant in the heat pump system has a low suction density at low evaporation temperatures. A common method to address this low-temperature performance reduction is medium-pressure gas injection technology. This technology introduces a portion of medium-pressure gas into the cylinder compression chamber through a medium-pressure gas injection channel. This gas mixes with the partially compressed refrigerant, is further compressed, and then discharged into the system. This increases the refrigerant flow rate in the condenser and the enthalpy difference in the heat pump system circuit. Consequently, rotary compressors using medium-pressure gas injection technology can significantly improve their low-temperature heating capacity and operate reliably over the long term, solving problems such as low-temperature heating capacity reduction and excessively high exhaust temperatures.

[0003] Existing medium-pressure gas-injected rotary compressors used in heat pump systems can effectively reduce the attenuation of heating capacity at low temperatures and improve low-temperature performance. Currently, there are two commonly used gas injection schemes for medium-pressure gas-injected rotary compressors: one is the roller cutting gas injection scheme, and the other is the check valve gas injection scheme. The check valve gas injection scheme typically involves arranging a gas injection channel and installing a gas injection check valve on the cylinder or pump body partition (dual cylinder). The check valve opens or closes the gas injection channel, thus enabling or disabling gas injection. For example, Chinese patent application CN105971879 B discloses a rotary compressor and its vane assembly, which includes a gas injection channel, valve plate, and baffle on the vane body; however, the gas injection effect of this scheme is unsatisfactory.

[0004] Accordingly, a new technical solution is needed in this field to solve the above problems. Summary of the Invention

[0005] This invention aims to solve the aforementioned technical problem, namely, the poor air replenishment effect of existing compressor air replenishment structures. To this end, this invention provides a cylinder with an air replenishment structure, comprising: a cylinder having a mounting groove on its end face facing the pump body partition; an axial air replenishment channel being provided at the bottom of the mounting groove; a radial air replenishment channel and a connecting groove also being provided on the cylinder; the two ends of the radial air replenishment channel being connected to an air replenishment device and the axial air replenishment channel, respectively; and the cross-sectional area of ​​the radial air replenishment channel being larger than that of the axial air replenishment channel; a valve cover being disposed within the mounting groove, forming a clearance space between the valve cover and the mounting groove; a flow groove being provided on the valve cover; and the clearance space being connected to the compression chamber through the flow groove and the connecting groove; and an air replenishment valve being openably and closably disposed between the clearance space and the axial air replenishment channel.

[0006] In a specific embodiment of the cylinder with the above-mentioned air replenishment structure, the air replenishment valve includes: a valve body disposed within the clearance space, the valve body having an installation through hole; and a valve plate located within the installation through hole, the valve plate including a connecting portion and a movable portion, one end of the connecting portion being disposed on the inner wall of the installation through hole, and the other end being connected to the movable portion, the movable portion being closably covering the air outlet of the axial air replenishment channel, the movable portion opening and closing under the pressure difference between the clearance space and the axial air replenishment channel.

[0007] In the specific embodiment of the cylinder with the above-mentioned air replenishment structure, the cross-section of the movable part is circular with a diameter of D, and the cross-section of the axial air replenishment channel is circular with a diameter of D1, wherein 0.5mm < D - D1 < 1mm.

[0008] In a specific embodiment of the cylinder with the above-mentioned air replenishment structure, a protrusion is provided on the valve cover, and the valve body located around the valve plate is pressed against the bottom surface of the mounting groove by the protrusion; a receiving groove is provided in the middle of the protrusion, and the clearance space is formed between the receiving groove and the mounting groove, and the movable part opens and closes within the clearance space.

[0009] In a specific embodiment of the cylinder with the above-mentioned air replenishment structure, the bottom surface of the receiving groove is inclined away from the moving part, and the end face of the protrusion adjacent to the valve body forms a certain angle θ with the bottom surface of the receiving groove, wherein 3° < θ < 12°.

[0010] In a specific embodiment of the cylinder with the above-mentioned air replenishment structure, the width of the receiving groove along the first direction is greater than the width of the connecting portion along the first direction.

[0011] In the specific embodiment of the cylinder with the above-mentioned air replenishment structure, the thickness of the valve cover along the axial direction is H1, wherein 3mm < H1 < 10mm; the depth of the flow groove along the axial direction is h, wherein 0.5mm < H1 - h < 1.5mm; the width of the flow groove along the first direction is W, wherein 1mm < W < 3mm; and / or the depth of the connecting groove along the axial direction is h1, wherein 1mm < h1 < 2mm; the width of the connecting groove along the first direction is M, wherein 1mm < M < 3mm.

[0012] In the specific embodiment of the cylinder with the above-mentioned air replenishment structure, the valve cover is made of an elastic material.

[0013] In the specific embodiment of the cylinder with the above-mentioned air replenishment structure, the radial length of the valve cover is greater than the radial length of the mounting groove.

[0014] In the specific embodiment of the cylinder with the above-mentioned air replenishment structure, the thickness of the air replenishment valve is H, the thickness of the valve cover is H1, and the depth of the mounting groove is H2, wherein 0.2 < H + H1 - H2 < 0.5 mm.

[0015] A compressor includes a first cylinder and a second cylinder formed by cylinders having a gas replenishment structure as described in any of the preceding claims, and a pump body partition; the first cylinder is axially disposed on one side of the second cylinder, and the pump body partition is disposed between the first cylinder and the second cylinder.

[0016] Solution 1. A cylinder with an air replenishment structure, characterized in that it comprises: a cylinder having an installation groove on its end face facing the pump body partition, an axial air replenishment channel being provided at the bottom of the installation groove, a radial air replenishment channel and a connecting groove being provided on the cylinder, the two ends of the radial air replenishment channel being connected to an air replenishment device and the axial air replenishment channel respectively, and the cross-sectional area of ​​the radial air replenishment channel being larger than the cross-sectional area of ​​the axial air replenishment channel; a valve cover being disposed in the installation groove, a clearance space being formed between the valve cover and the installation groove, a flow groove being provided on the valve cover, and the clearance space being connected to the compression chamber through the flow groove and the connecting groove; and an air replenishment valve being openably and closably disposed between the clearance space and the axial air replenishment channel.

[0017] Option 2. The cylinder with a replenishing air structure according to Option 1, characterized in that the replenishing air valve includes: a valve body disposed within the clearance space, the valve body having an installation through hole; a valve plate located within the installation through hole, the valve plate including a connecting portion and a movable portion, one end of the connecting portion being disposed on the inner wall of the installation through hole, the other end being connected to the movable portion, the movable portion being closably covering the air outlet of the axial replenishing air channel, the movable portion opening and closing under the pressure difference between the clearance space and the axial replenishing air channel.

[0018] Scheme 3. The cylinder with an air replenishment structure according to Scheme 2, characterized in that the cross-section of the movable part is circular with a diameter of D, and the cross-section of the axial air replenishment channel is circular with a diameter of D1, wherein 0.5mm < D - D1 < 1mm.

[0019] Solution 4. The cylinder with a replenishing air structure according to Solution 2, characterized in that a protrusion is provided on the valve cover, and the valve body located around the valve plate is abutted against the bottom surface of the mounting groove by the protrusion; a receiving groove is provided in the middle of the protrusion, and the receiving groove and the mounting groove form the clearance space, and the movable part opens and closes within the clearance space.

[0020] Scheme 5. The cylinder with an air replenishment structure according to Scheme 4, characterized in that the bottom surface of the receiving groove is inclined away from the moving part, and the end face of the protrusion adjacent to the valve body forms a certain angle θ with the bottom surface of the receiving groove, wherein 3° < θ < 12°.

[0021] Solution 6. The cylinder with an air replenishment structure according to Solution 4, characterized in that the width of the receiving groove along the first direction is greater than the width of the connecting portion along the first direction.

[0022] Scheme 7. The cylinder with an air replenishment structure according to Scheme 1, characterized in that: the thickness of the valve cover along the axial direction is H1, wherein 3mm < H1 < 10mm; the depth of the flow groove along the axial direction is h, wherein 0.5mm < H1 - h < 1.5mm; the width of the flow groove along the first direction is W, wherein 1mm < W < 3mm; and / or the depth of the connecting groove along the axial direction is h1, wherein 1mm < h1 < 2mm; the width of the connecting groove along the first direction is M, wherein 1mm < M < 3mm.

[0023] Option 8. The cylinder with an air replenishment structure according to Option 1, characterized in that the valve cover is made of an elastic material.

[0024] Solution 9. The cylinder with a replenishing air structure according to Solution 8, characterized in that the radial length of the valve cover is greater than the radial length of the mounting groove.

[0025] Scheme 10. The cylinder with an air replenishment structure according to Scheme 8, characterized in that the thickness of the air replenishment valve is H, the thickness of the valve cover is H1, and the depth of the mounting groove is H2, wherein 0.2 < H + H1 - H2 < 0.5 mm.

[0026] Solution 11. A compressor, characterized in that it comprises a first cylinder and a second cylinder formed by cylinders having a gas replenishment structure as described in any one of Solutions 1-10, and a pump body partition; the first cylinder is axially disposed on one side of the second cylinder, and the pump body partition is disposed between the first cylinder and the second cylinder.

[0027] By adopting the above technical solution, this invention improves the air replenishment effect of the air replenishment structure by adjusting the cross-sectional area of ​​the radial air replenishment channel and the cross-sectional area of ​​the axial air replenishment channel. Since the two ends of the radial air replenishment channel are connected to the air replenishment device and the axial air replenishment channel respectively, the larger the cross-sectional area of ​​the radial air replenishment channel, the greater the amount of air replenished from the air replenishment device into the radial air replenishment channel, and the better the air replenishment effect. Although increasing the cross-sectional area of ​​the axial air replenishment channel can also increase the air replenishment effect, since the axial air replenishment channel is located close to the inside of the cylinder, increasing the size of the axial air replenishment channel would greatly increase the processing difficulty. Therefore, this invention limits the size of the axial air replenishment channel and increases the cross-sectional area of ​​the radial air replenishment channel, effectively improving the air replenishment effect of the air replenishment structure and enhancing the low-temperature heating performance.

[0028] Furthermore, in this embodiment, the mounting groove is directly set on the end face of the cylinder, and the axial air supply channel, radial air supply channel and connecting groove are directly set on the cylinder. Compared with the method of setting them on the sliding vane and then installing the sliding vane in the sliding vane groove, the solution in this embodiment is easier to design and manufacture. Moreover, the valve cover is installed between the mounting groove and the pump body partition, which makes the installation method more reliable and the sealing performance better. Attached Figure Description

[0029] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

[0030] Figure 1 This is a schematic diagram of the cylinder structure in this invention;

[0031] Figure 2 This is a front structural diagram of the cylinder in this invention;

[0032] Figure 3 This is a cross-sectional structural diagram of the cylinder in this invention at a certain angle;

[0033] Figure 4 This is a schematic diagram of the valve cover structure in this invention;

[0034] Figure 5 This is a front structural diagram of the air replenishment valve in this invention;

[0035] Figure 6 This is a schematic diagram of the structure of the air supply valve and valve cover after assembly in this invention;

[0036] Figure 7 yes Figure 6 Cross-sectional view at point AA;

[0037] Figure 8 This is a cross-sectional view of the cylinder with the air replenishment structure in this invention from a certain perspective.

[0038] Figure 9 yes Figure 8 Enlarged view of point B in the middle;

[0039] Figure 10 This is a schematic diagram of the compressor in this invention.

[0040] In the diagram: 1. Cylinder; 11. Mounting groove; 12. Axial air supply channel; 13. Radial air supply channel; 14. Connecting groove; 2. Valve cover; 21. Clearance space; 22. Protrusion; 23. Receiving groove; 24. Flow groove; 3. Air supply valve; 31. Valve body; 32. Mounting through hole; 33. Valve plate; 34. Connecting part; 35. Moving part; 41. First cylinder; 42. Second cylinder; 43. Pump body partition; 44. Air supply device; 45. Crankshaft; 46. Upper bearing assembly; 47. Lower bearing assembly; 48. Housing. Detailed Implementation

[0041] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. Those skilled in the art can make adjustments as needed to adapt to specific application scenarios.

[0042] It should be noted that in the description of this invention, terms such as "upper," "lower," "left," "right," "inner," and "outer," which indicate direction or positional relationships, are based on the direction or positional relationships shown in the accompanying drawings. These are used merely for ease of description and do not indicate or imply that the relevant devices or elements must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention. Furthermore, ordinal numbers such as "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0043] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "installation" and "connection" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0044] Furthermore, in order to more clearly demonstrate the core technical solution of the present invention, the description of the known structure of the compressor is omitted in the following description. However, this omission is only for the convenience of description and does not mean that the compressor can be without these structures.

[0045] like Figure 1-9 As shown, the present invention proposes a cylinder with a gas replenishment structure, comprising: a cylinder 1, which has an installation groove 11 on its end face facing the pump body partition 43, an axial gas replenishment channel 12 at the bottom of the installation groove 11, a radial gas replenishment channel 13 and a connecting groove 14 on the cylinder 1, one end of the radial gas replenishment channel 13 being connected to a gas replenishment device 44, which is a gas replenishment liquid separator, and the other end being connected to the axial gas replenishment channel 12, wherein the cross-sectional area of ​​the radial gas replenishment channel 13 is larger than the cross-sectional area of ​​the axial gas replenishment channel 12; a valve cover 2, which is disposed in the installation groove 11, forming a clearance space 21 between the valve cover 2 and the installation groove 11, and a flow groove 24 on the valve cover 2, the clearance space 21 being connected to the compression chamber through the flow groove 24 and the connecting groove 14; and a gas replenishment valve 3, which is closably disposed between the clearance space 21 and the axial gas replenishment channel 12.

[0046] The medium-pressure gas in the gas replenishment device 44 enters the radial gas replenishment channel 13 and the axial gas replenishment channel 12 in sequence. If the gas replenishment valve 3 is closed, the clearance space 21 and the axial gas replenishment channel 12 are not connected, and the medium-pressure gas cannot flow into the clearance space 21 and cannot be replenished. If the gas replenishment valve 3 is open, the clearance space 21 and the axial gas replenishment channel 12 are connected, and the medium-pressure gas flows from the axial gas replenishment channel 12 into the clearance space 21, and then flows into the compression chamber of the cylinder 1 through the connecting groove 14 for gas replenishment.

[0047] In this embodiment, to address the problem of poor air replenishment effect in existing air replenishment structures, the cross-sectional area of ​​the radial air replenishment channel 13 is set to be larger than that of the axial air replenishment channel 12. This is because the two ends of the radial air replenishment channel 13 are connected to the air replenishment device 44 and the axial air replenishment channel 12, respectively. A larger cross-sectional area of ​​the radial air replenishment channel 13 allows for a greater amount of air replenishment from the air replenishment device 44 into the radial air replenishment channel 13, resulting in a better air replenishment effect. Increasing the cross-sectional area of ​​the axial air replenishment channel 12 can also improve the air replenishment effect. However, since the axial air replenishment channel 12 is located close to the inside of the cylinder, increasing its size would significantly increase the manufacturing difficulty. Therefore, in this embodiment, the preferred range for the diameter D1 of the axial air replenishment channel 12 is: 2mm ≤ D1 ≤ 5mm.

[0048] Furthermore, in this embodiment, the mounting groove 11 is directly set on the end face of the cylinder 1, and the axial air supply channel 12, radial air supply channel 13 and connecting groove 14 are directly set on the cylinder 1. Compared with the method of setting them on the sliding plate and then installing the sliding plate in the sliding plate groove, the solution in this embodiment is easier to design and process. Moreover, the valve cover 2 is installed between the mounting groove 11 and the pump body partition 43. This installation method is more reliable and has better sealing performance.

[0049] In this embodiment, by adjusting the cross-sectional area of ​​the radial air supply channel 13 and the cross-sectional area of ​​the axial air supply channel 12, the air supply effect of the air supply structure can be effectively improved, the low-temperature heating performance can be enhanced, and the design and processing can be facilitated.

[0050] When both the radial air supply channel 13 and the axial air supply channel 12 have circular cross-sections, the diameter of the radial air supply channel 13 is greater than the diameter of the axial air supply channel 12, which makes the cross-sectional area of ​​the radial air supply channel 13 greater than the cross-sectional area of ​​the axial air supply channel 12.

[0051] It should be noted that, Figure 3 Both the radial air supply channel 13 and the axial air supply channel 12 have circular cross-sections. However, this is not a limitation of the present invention. Without departing from the basic principles of the present invention, those skilled in the art can set the cross-sections of the radial air supply channel 13 and the axial air supply channel 12 to other shapes, as long as the air supply device 44 can be connected to the clearance space 21 and the cross-sectional area of ​​the radial air supply channel 13 is greater than the cross-sectional area of ​​the axial air supply channel 12. For example, setting the cross-sections of the radial air supply channel 13 and / or the axial air supply channel 12 to rectangles, etc., does not depart from the principles of the present invention and therefore falls within the protection scope of the present invention.

[0052] Furthermore, such as Figure 5As shown, in this embodiment, the air replenishment valve 3 includes: a valve body 31, which is disposed in the clearance space 21 and has an installation through hole 32; and a valve plate 33, which is located in the installation through hole 32. The valve plate 33 includes a connecting part 34 and a movable part 35. One end of the connecting part 34 is disposed on the inner wall of the installation through hole 32, and the other end is connected to the movable part 35. The movable part 35 is closably covered on the air outlet of the axial air replenishment channel 12. The movable part 35 is opened and closed under the pressure difference between the clearance space 21 and the axial air replenishment channel 12.

[0053] When the replenishment pressure is less than the refrigerant pressure in the cylinder volume, the pressure in the axial replenishment channel 12 is less than the pressure in the clearance space 21. Under the action of the pressure difference, the movable part 35 in the clearance space 21 covers the outlet of the axial replenishment channel 12, the replenishment valve 3 is closed, the clearance space 21 and the axial replenishment channel 12 are not connected, the medium-pressure gas cannot flow into the clearance space 21, and replenishment cannot be performed.

[0054] When the replenishment pressure is greater than the refrigerant pressure in the cylinder volume, the pressure in the axial replenishment channel 12 is greater than the pressure in the clearance space 21. The movable part 35 in the clearance space 21 is blown toward the valve cover 2 under the action of the pressure difference, the replenishment valve 3 opens, and the clearance space 21 is connected to the axial replenishment channel 12. The medium-pressure gas flows from the axial replenishment channel 12 into the clearance space 21, and then flows into the compression chamber of the cylinder 1 through the connecting groove 14 for replenishment.

[0055] Furthermore, when the cross-sectional shape of the axial air supply channel 12 is circular, its diameter is D1, and the cross-section of the movable part 35 is also circular, with a diameter of D. In this embodiment, in order to enable the movable part 35 to completely cover the air outlet of the axial air supply channel 12 and enhance the sealing performance of the air supply structure to prevent air leakage, D needs to be greater than D1. However, the movable part 35 cannot be too large, as this would increase the force required when it is blown up. Therefore, the difference between the diameter of the axial air supply channel 12 and the diameter of the movable part 35 is limited to: 0.5mm < D - D1 < 1mm.

[0056] It should be noted that although the diameter of the axial air supply channel 12 is specified above, those skilled in the art can use other shapes of movable parts 35 without departing from the basic principles of the present invention, as long as the movable part 35 can cover the axial air supply channel 12. For example, the cross-section of the movable part 35 can be set to rectangular, etc., which do not depart from the principles of the present invention and therefore will fall within the protection scope of the present invention.

[0057] Furthermore, such as Figure 4 As shown, in order to better fix the air supply valve 3, the valve cover 2 is provided with a protrusion 22, and the valve body 31 located around the valve plate 33 is pressed against the bottom surface of the mounting groove 11 by the protrusion 22. Figure 4A flow groove 24 is provided on the protrusion 22 at a position corresponding to the connecting groove 14, so that the clearance space 21 is connected to the connecting groove 14. A receiving groove 23 is provided in the middle of the protrusion 22, and the valve plate 33 is received in the receiving groove 23. The receiving groove 23 and the mounting groove 11 form a clearance space 21, and the movable part 35 opens and closes within the clearance space 21.

[0058] Furthermore, such as Figure 9 As shown, the bottom surface of the receiving groove 23 is inclined away from the moving part 35. The end face of the protrusion 22 adjacent to the valve body 31 forms a certain angle θ with the bottom surface of the receiving groove 23, where 3° < θ < 12°. The bottom surface of the receiving groove 23 is used to limit the lift of the moving part 35. Therefore, the angle θ cannot be too large or too small. If it is too small, it will easily lead to unsmooth air supply. If it is too large, it will be difficult for the moving part 35 to return to the initial position, which will result in the inability to accurately cover the axial air supply channel 12. Therefore, setting the range of θ to 3° < θ < 12° is more appropriate.

[0059] Furthermore, such as Figure 6-7 As shown, the width of the receiving groove 23 along the first direction is greater than the width of the connecting part 34 along the first direction. Since the middle of the protrusion 22 is the receiving groove 23, this can avoid the protrusion 22 interfering with the opening of the connecting part 34. Figure 7 The X direction is used to represent the first direction.

[0060] The position on the mounting through hole 32 corresponding to the connection between the movable part 35 and the connecting part 34 has a width difference of ΔL with the inner wall of the receiving groove 23 in the first direction, where 0.3mm < ΔL < 0.6mm. The smaller the width of the connection between the movable part 35 and the connecting part 34 in the first direction, the smaller the force required for the movable part 35 to be blown up.

[0061] Furthermore, the cross-sectional area of ​​the flow channel 24 and / or the connecting channel 14 cannot be too small. If it is too small, it will obstruct the air supply, resulting in high flow resistance and large air supply loss. However, the cross-sectional area of ​​the flow channel 24 and / or the connecting channel 14 cannot be too large either. If it is too large, it will increase the clearance volume of the air supply and reduce the energy efficiency of the compressor. In this embodiment, preferably: the thickness of the valve cover 2 along the axial direction is H1, where 3mm < H1 < 10mm; the depth of the flow channel 24 along the axial direction is h, where 0.5mm < H1 - h < 1.5mm; the width of the flow channel 24 along the first direction is W, where 1mm < W < 3mm. The depth of the connecting channel 14 along the axial direction is h1, where 1mm < h1 < 2mm; the width of the connecting channel 14 along the first direction is M, where 1mm < M < 3mm.

[0062] To avoid axial height assembly errors, the depth of the flow groove 24 is slightly greater than the depth of the connecting groove 14.

[0063] like Figure 5-7 As shown, since the valve plate 33 includes two parts, a connecting part 34 and a movable part 35, in order to cover the axial air supply channel 12, the size of the movable part 35 is larger than the size of the axial air supply channel 12. In order to facilitate the blowing of the movable part 35, the width of the connecting part 34 along the first direction is relatively narrow. In order to reduce the air supply clearance volume formed by the receiving groove 23 and the flow groove 24, the shape of the connecting groove 14 has also been adapted. The connecting groove 14 is also divided into two parts: the first groove is wider along the first direction to accommodate the movable part 35, and the second groove is narrower along the first direction to accommodate the connecting part 34. Figure 4-6 As shown, for ease of processing and manufacturing, the first groove and the cross-section of the first groove are rectangular.

[0064] It should be pointed out that, although Figure 4 and Figure 6 The first groove and its cross-section shown are rectangular, but this is not a limitation of the present invention. Without departing from the basic principles of the present invention, those skilled in the art can set the first groove and its cross-section to other shapes, as long as it does not affect the opening and closing of the valve plate 33. For example, the cross-sectional shape of the first groove can be the same as the cross-sectional shape of the movable part 35, such as a circle, etc. These do not depart from the principles of the present invention and therefore fall within the protection scope of the present invention.

[0065] Furthermore, the valve cover 2 is made of an elastic material. The elastic material can be rubber or similar materials, and the hardness of the valve cover 2 can be 20HS to 40HS. In this embodiment, the elastic valve cover 2 can effectively fix the air supply valve 3 and reduce the air supply clearance volume between the valve cover 2 and the mounting groove 11, thereby improving the volumetric efficiency and performance of the compressor.

[0066] Furthermore, when the valve cover 2 is made of an elastic material, the radial length of the valve cover 2 is slightly greater than the radial length of the mounting groove 11. This way, after the valve cover 2 is installed in the mounting groove 11, a gap can be avoided between the valve cover 2 and the mounting groove 11. The gas supplied can then pass through the flow groove 24 and directly enter the compression chamber through the connecting groove 14, preventing the supplied gas from entering the gap between the valve cover 2 and the mounting groove 11 and creating additional gas supply clearance, which would affect the gas supply effect.

[0067] Furthermore, the thickness of the air supply valve 3 is H, the thickness of the valve cover 2 is H1, and the depth of the mounting groove 11 is H2, where 0.2 < H + H1 - H2 < 0.5 mm. Since the valve cover 2 is made of an elastic material, the sum of the thickness of the air supply valve 3 and the valve cover 2 is slightly greater than the depth of the mounting groove 11. This allows the valve cover 2 to deform during installation, making the installation more stable and allowing the air supply valve 3 to be better secured.

[0068] During installation, cylinder 1 is installed adjacent to pump body partition 44, and valve cover 2 is installed in the mounting groove 11 on the end face of cylinder 1 facing pump body partition 43. When the sum of the thickness of the air supply valve 3 and the thickness of valve cover 2 is slightly greater than the depth of mounting groove 11, the air supply valve 3 will be squeezed and undergo elastic deformation during installation, making the installation more stable. It can also prevent gaps from appearing in valve cover 2, reduce the air supply clearance volume, and improve compressor performance.

[0069] A compressor includes a first cylinder 41 and a second cylinder 42 formed by cylinders having a gas-injection structure as described above, and a pump body partition 43; the first cylinder 41 is axially disposed on one side of the second cylinder 42, and the pump body partition 43 is disposed between the first cylinder 41 and the second cylinder 42; it also includes: a gas-injection device 44 communicating with the gas-injection structure, a crankshaft 45 disposed in the cylinder, an upper bearing assembly 46 and a lower bearing assembly 47 for supporting the crankshaft 45, and a compressor housing 48.

[0070] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A cylinder with an air-injection structure, characterized in that, include: The cylinder (1) has an installation groove (11) on its end face facing the pump body partition (43). An axial air supply channel (12) is provided at the bottom of the installation groove (11). The cylinder (1) is also provided with a radial air supply channel (13) and a connecting groove (14). The two ends of the radial air supply channel (13) are respectively connected to the air supply device (44) and the axial air supply channel (12). The cross-sectional area of ​​the radial air supply channel (13) is larger than the cross-sectional area of ​​the axial air supply channel (12). A valve cover (2) is disposed in the mounting groove (11), and a clearance space (21) is formed between the valve cover (2) and the mounting groove (11). A flow groove (24) is provided on the valve cover (2), and the clearance space (21) is connected to the compression chamber through the flow groove (24) and the connecting groove (14). An air supply valve (3) is provided openably and closably between the clearance space (21) and the axial air supply channel (12).

2. The cylinder with an air-injection structure according to claim 1, characterized in that, The air supply valve (3) includes: Valve body (31), the valve body (31) is disposed in the clearance space (21), and the valve body (31) is provided with a mounting through hole (32); Valve plate (33) is located in the mounting through hole (32). The valve plate (33) includes a connecting part (34) and a movable part (35). One end of the connecting part (34) is disposed on the inner wall of the mounting through hole (32), and the other end is connected to the movable part (35). The movable part (35) is closably covered on the air outlet of the axial air supply channel (12). The movable part (35) is opened and closed under the pressure difference between the clearance space (21) and the axial air supply channel (12).

3. The cylinder with an air-injection structure according to claim 2, characterized in that, The cross-section of the movable part (35) is circular with a diameter of D, and the cross-section of the axial air supply channel (12) is circular with a diameter of D1, wherein 0.5mm < D - D1 < 1mm.

4. The cylinder with an air-injection structure according to claim 2, characterized in that, The valve cover (2) is provided with a protrusion (22), and the valve body (31) located around the valve plate (33) is pressed against the bottom surface of the mounting groove (11) by the protrusion (22); The protrusion (22) has a receiving groove (23) in the middle, and the receiving groove (23) and the mounting groove (11) form the clearance space (21), and the movable part (35) opens and closes within the clearance space (21).

5. The cylinder with an air-injection structure according to claim 4, characterized in that, The bottom surface of the receiving groove (23) is inclined away from the moving part (35), and the end face of the protrusion (22) adjacent to the valve body (31) forms a certain angle θ with the bottom surface of the receiving groove (23), wherein 3° < θ < 12°.

6. The cylinder with an air-injection structure according to claim 4, characterized in that, The width of the receiving groove (23) along the first direction is greater than the width of the connecting part (34) along the first direction.

7. The cylinder with an air-injection structure according to claim 1, characterized in that, The valve cover (2) has an axial thickness of H1, where 3mm < H1 < 10mm; the flow groove (24) has an axial depth of h, where 0.5mm < H1 - h < 1.5mm; the flow groove (24) has a width of W in the first direction, where 1mm < W < 3mm; and / or The depth of the connecting groove (14) along the axial direction is h1, where 1mm < h1 < 2mm; the width of the connecting groove (14) along the first direction is M, where 1mm < M < 3mm.

8. The cylinder with an air-injection structure according to claim 1, characterized in that, The valve cover (2) is made of elastic material.

9. The cylinder with an air-injection structure according to claim 8, characterized in that, The radial length of the valve cover (2) is greater than the radial length of the mounting groove (11).

10. The cylinder with an air-injection structure according to claim 8, characterized in that, The thickness of the air supply valve (3) is H, the thickness of the valve cover (2) is H1, and the depth of the mounting groove (11) is H2, wherein 0.2 < H + H1 - H2 < 0.5 mm.

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