Pump body assembly, compressor and air conditioner having the same

Abstract

The present application provides a pump assembly, a compressor, and an air conditioner equipped therewith, each comprising a cylinder structure having an air intake passage disposed therein. The air intake passage extends from the outer periphery of the cylinder structure to the inner periphery of the cylinder structure, and is capable of guiding gas from the outside of the cylinder structure into the interior of the cylinder structure. The air intake passage extends in an angle with the radial direction of the cylinder structure. The pump assembly, compressor, and air conditioner equipped therewith according to the present application can improve the operating efficiency of the compressor.

Description

Technical Field

[0001] The present application belongs to the technical field of air conditioners, and in particular relates to a pump assembly, a compressor, and an air conditioner having the same. Background Art

[0002] At present, the latest mandatory national standards for air conditioner energy efficiency have increasingly higher requirements for compressor performance, and more ways to improve efficiency need to be opened up.

[0003] However, the cylinder of the rotary compressor in the related art usually adopts a radial suction hole opened on one side of the sliding vane groove. During the suction process of the compressor, there is a large backflow and turbulence loss, which is not conducive to improving the energy efficiency of the compressor.

[0004] Therefore, how to provide a pump assembly, a compressor and an air conditioner having the same that can improve the working efficiency of the compressor has become a problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0005] Therefore, the technical problem to be solved by the present application is to provide a pump body assembly, a compressor and an air conditioner having the same, which can improve the working efficiency of the compressor.

[0006] In order to solve the above problems, the present application provides a pump body assembly, including a cylinder structure, on which an intake channel is provided; the intake channel extends from the outer peripheral side of the cylinder structure to the inner peripheral side of the cylinder structure, and the intake channel can guide the gas from the outside of the cylinder structure into the inside of the cylinder structure; and there is an angle between the extension direction of the intake channel and the radial direction of the cylinder structure.

[0007] Furthermore, a vane groove is provided on the cylinder structure; the vane groove extends in the radial direction of the cylinder structure; and the air intake channel extends from one circumferential side of the vane groove to the other circumferential side of the vane groove.

[0008] Furthermore, the pump body assembly also includes a connecting pipe, which is arranged in the through hole and connects the first section and the second section; during the movement of the sliding vane structure, the position of the connecting pipe remains unchanged.

[0009] Furthermore, the first section extends from the sliding vane groove to the outer peripheral wall of the cylinder structure, and the cross-sectional area of ​​the first section gradually increases in a direction approaching the outer peripheral wall of the cylinder structure.

[0010] Furthermore, the connecting pipe extends from the first section through the through hole to the second section; the connecting pipe is provided with a necking section; or

[0011] Among them, s1 is the inlet cross-sectional area of ​​the connecting pipe, s2 is the cross-sectional area of ​​the necking section; s3 is the maximum cross-sectional area of ​​the outlet of the connecting pipe; h1 is the enthalpy value of the inlet cross-sectional area of ​​the connecting pipe; h2 is the enthalpy value of the minimum cross-sectional area of ​​the necking section of the connecting pipe; h3 is the enthalpy value of the outlet cross-sectional area of ​​the connecting pipe; ρ2 is the density of the minimum cross-sectional area of ​​the necking section of the connecting pipe; ρ3 is the density of the outlet cross-sectional area of ​​the connecting pipe, and the axial height of the cylinder structure is h.

[0012] Furthermore, the pump body assembly further includes a crankshaft, the eccentricity of the crankshaft is e; in the movable direction of the vane structure, the minimum length of the through hole is L1; the minimum distance between the through hole and the radial outer surface of the vane structure is L2; ​​the inner diameter of the cylinder structure is D, and the axial height of the cylinder structure is h; the pump body assembly further includes a roller structure, and the outer diameter of the roller structure is d;

[0013] Among them, L1≥2e;

[0014] and / or,

[0015] and / or,

[0016] Furthermore, the angle between the air intake channel and a perpendicular line to the extending direction of the vane slot is θ; 0.25≤|cosθ|<1.

[0017] Furthermore, the outer wall of the connecting pipe is at least partially in contact with the inner wall of the air intake passage.

[0018] According to another aspect of the present application, a compressor is provided, comprising a pump body assembly, which is the above-mentioned pump body assembly.

[0019] According to another aspect of the present application, an air conditioner is provided, comprising a compressor, which is the above-mentioned compressor.

[0020] The pump body assembly, compressor and air conditioner having the same provided in this application can improve the working efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 This is a schematic structural diagram of the cylinder structure of an embodiment of the present application;

[0022] Figure 2 This is a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0023] Figure 3 This is a schematic structural diagram of the sliding structure of an embodiment of the present application;

[0024] Figure 4 This is a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0025] Figure 5 This is a schematic structural diagram of a connecting pipe according to an embodiment of the present application;

[0026] Figure 6 This is a schematic structural diagram of a connecting pipe according to an embodiment of the present application;

[0027] Figure 7 This is a schematic structural diagram of a connecting pipe according to an embodiment of the present application;

[0028] Figure 8 This is a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0029] Figure 9 This is a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0030] Figure 10 This is a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0031] Figure 11 This is a schematic structural diagram of a connecting pipe according to an embodiment of the present application;

[0032] Figure 12 Schematic diagrams of air intake in three implementation modes of the present application and related technologies;

[0033] Figure 13 This is a structural comparison diagram of the relevant scheme and this scheme;

[0034] Figure 14 Schematic diagram of the structure of the air intake channel at various inclination angles in an embodiment of the present application;

[0035] Figure 15 This is a line graph showing the relationship between the inclination angle of the intake channel and the intake loss pressure drop according to an embodiment of the present application.

[0036] The reference numerals indicate:

[0037] 1. Cylinder structure; 2. Vane groove; 3. Intake channel; 4. Connecting pipe; 5. Vane structure; 51. Through hole; 6. Roller structure; 7. Upper flange; 8. Lower flange; 9. Crankshaft. DETAILED DESCRIPTION

[0038] See also Figure 1-15As shown, a pump body assembly includes a cylinder structure 1, on which an air intake channel 3 is provided; the air intake channel 3 extends from the outer peripheral side of the cylinder structure 1 to the inner peripheral side of the cylinder structure 1, and the air intake channel 3 can guide the gas from the outside of the cylinder structure 1 into the inside of the cylinder structure 1; and there is an angle between the extension direction of the air intake channel 3 and the radial direction of the cylinder structure 1. The present application can make the air intake smoother, reduce the flow resistance of the cylinder, reduce the disordered movement of the compressed medium, thereby reducing energy loss and improving the working efficiency of the compressor. The present application can reduce the turbulent loss problem in the air intake process of the compressor.

[0039] For the suction opening angle: This application adopts the method of beveling the suction port, and the axis of the suction port does not need to pass through the center of the cylinder, so the minimum suction angle can be The traditional air intake port needs to avoid the spring, and the spring radius is usually dt = kd / 2 (k is 2 to 3), and the spring hole and the center S of the cylinder are generally bD (b is 1.5 to 2), so that the minimum air intake angle is

[0040]

[0041] Regarding the intake closing angle: the intake closing angle is numerically equal to the sum of the intake opening angle and the intake range angle. Therefore, at the same intake range angle, the intake closing angle corresponds to the intake opening angle. The smaller the intake angle, the smaller the intake closing angle. The advantage of a small intake closing angle is that it increases the volume of the working chamber, strengthens the work capacity of a single cylinder, and improves the volumetric efficiency of the compressor. Under the same conditions, the oblique intake port is larger than the radial intake port.

[0042] This application also discloses some embodiments in which the cylinder structure 1 is further provided with a vane slot 2; the vane slot 2 extends in the radial direction of the cylinder structure 1; and the air intake passage 3 extends from one circumferential side of the vane slot 2 to the other circumferential side of the vane slot 2. In other words, the air intake passage 3 obliquely penetrates the vane slot 2. The oblique direction in this application refers to an inclination relative to the radial direction of the cylinder structure 1.

[0043] This application also discloses certain embodiments, wherein the pump assembly further includes a vane structure 5 movably disposed within the cylinder structure 1 and dividing the interior of the cylinder structure 1 into an intake chamber and an exhaust chamber. The intake passage 3 comprises a first section and a second section, with the first section located on one circumferential side of the vane slot 2 and the second section located on the other circumferential side of the vane slot 2. A through hole 51 is formed in the vane structure 5, connecting the first and second sections. The through hole 51 formed in the vane structure 5 and the cylinder vane slot 2 reduces the contact area between the vane structure 5 and the cylinder structure 1, reducing mechanical friction and improving the mechanical efficiency of the pump, thereby enhancing the energy efficiency of the compressor. This application reduces mechanical friction between the vane structure 5 and the cylinder structure 1, thereby improving mechanical efficiency. The device is relatively simple, easy to assemble, and low-cost. Furthermore, gas can enter the internal compression chamber of the cylinder structure 1 sequentially from the first section, through hole 51, and second section. The through hole 51 serves to connect the intake passage 3.

[0044] The present application also discloses some embodiments in which the pump assembly further includes a connecting pipe 4, which is disposed within a through hole 51 and connects the first section and the second section. The position of the connecting pipe 4 remains unchanged during the movement of the vane structure 5. During the movement of the vane structure 5, the through hole 5 provides a clearance for the connecting pipe 4, preventing the vane structure 5 from colliding with the connecting pipe 4 and affecting its position. Furthermore, the connecting pipe 4 enables smooth air intake in the air intake passage 3, preventing gas within the air intake passage 3 from leaking through the vane slot 2.

[0045] The present application also discloses some embodiments, in which the first section extends from the vane groove 2 to the outer wall of the cylinder structure 1, and the cross-sectional area of ​​the first section gradually increases in the direction close to the outer wall of the cylinder structure 1. The present application solves the problem occurring at the air intake of the compressor, with smooth air intake, smaller flow resistance, lower pressure loss, and less friction between the vane structure 5 and the cylinder structure 1, which has a positive impact on improving the energy efficiency of the compressor. The present application can also advance the intake opening angle and closing angle, reduce the clearance volume at the air intake, improve volumetric efficiency, and increase the working volume, which is conducive to miniaturization of the model. The design structure is relatively simple, the assembly is relatively simple, and the operability is strong.

[0046] The connecting pipe 4 and the oblique air intake port, namely the air intake channel 3 of the present application can be derived into a special-shaped pipe and a special-shaped groove respectively.

[0047] The present application also discloses some embodiments, wherein the connecting pipe 4 extends from the first section through the through hole 51 to the second section; the connecting pipe 4 is provided with a necking section; or

[0048] Among them, s1 is the inlet cross-sectional area of ​​the connecting pipe 4, s2 is the cross-sectional area of ​​the necking section; s3 is the maximum cross-sectional area of ​​the outlet of the connecting pipe 4; h1 is the enthalpy value of the inlet cross-sectional area of ​​the connecting pipe 4; h2 is the enthalpy value of the minimum cross-sectional area of ​​the necking section of the connecting pipe 4; h3 is the enthalpy value of the outlet cross-sectional area of ​​the connecting pipe 4; ρ2 is the density of the minimum cross-sectional area of ​​the necking section of the connecting pipe 4; ρ3 is the density of the outlet cross-sectional area of ​​the connecting pipe 4, and the axial height of the cylinder structure 1 is h.

[0049] The connecting pipe 4 of the present application forms the first section of the suction port channel 3 - the connecting pipe 4 - the suction chamber constitutes a nozzle structure. During the suction process of the compressor, the volume of the suction chamber continues to increase as the rotor rotation angle increases. The pressure in the chamber is always lower than the suction pressure, and a large amount of compressed working fluid flows into the compression chamber. The suction process takes a very short time (generally 0.02s), which can be approximated as an isentropic process. According to the law of conservation of mass, the mass flow rate is large where the flow area is small. Because the flow path is all gaseous refrigerant, the density magnitude difference is very small, so the flow rate is also relatively large where the flow area is small. According to the Bernoulli equation, the greater the flow rate of the circulating medium, the lower the pressure. Therefore, the nozzle can convert part of the internal energy into kinetic energy, and the flowing medium is more likely to flow into the compression chamber. Therefore, it has a more significant effect in high-frequency low-temperature heating. Another beneficial effect is that the nozzle can reduce the suction pressure and temperature. Combined with the use of the beveled suction port, the suction can be made smoother and faster. At the same time, the exhaust temperature will also decrease accordingly with the decrease in suction pressure and temperature, and the reliability of the compressor is improved.

[0050] The present application also discloses some embodiments, wherein the pump body assembly further comprises a crankshaft 9, the eccentricity of the crankshaft 9 being e; the minimum length of the through hole 51 in the movable direction of the vane structure 5 being L1; the minimum distance between the through hole 51 and the radial outer surface of the vane structure 5 being L2; the inner diameter of the cylinder structure 1 being D, and the axial height of the cylinder structure 1 being h; the pump body assembly further comprises a roller structure 6, the outer diameter of the roller structure 6 being d;

[0051] Wherein, L1≥2e; interference between the movement of the sliding structure 5 and the connecting pipe 4 can be avoided.

[0052] This application also discloses some embodiments.

[0053] This application also discloses some embodiments. This can prevent the high-pressure and low-pressure chambers from being connected when the sliding structure 5 is stretched to the maximum.

[0054] The present application also discloses some embodiments, in which the angle between the air intake channel 3 and the perpendicular line to the extension direction of the vane slot 2 is θ; 0.25≤|cosθ|<1.

[0055] Attachment Figure 14-15The cylinder pressure drop level in FIG is obtained based on simulation tests. The cross-sectional area of ​​each intake channel 5 is the same to avoid the influence of the intake cross-sectional flow velocity on the along-the-line resistance.

[0056] The following is based on air as the medium, and the suction cross-sectional area is 132.7mm 2 ,The suction pressure drop data of different oblique cut angles were obtained under the test conditions of cross-sectional flow velocity of 0.5m / s.

[0057]

[0058] The suction flow rate is related to the compressor displacement, the working medium suction state, and the suction cross-section. The average suction flow rate of the compressor is generally 0.5 to 10 m / s. According to the calculation formula of local and along-the-line loss, when the flow rate is large, the along-the-line loss can be amplified by hundreds of times, so the reduction of the oblique suction pressure loss will have a more significant effect.

[0059] Darcy-Weisbach formula for along-the-line losses

[0060] λ is the drag coefficient along the flow path, which is related to the Reynolds number of the flow and the roughness of the wall;

[0061] l is the length of the pipeline;

[0062] d is the equivalent diameter of the pipe;

[0063] V is the average flow velocity in the effective cross section;

[0064] g is the acceleration due to gravity;

[0065] local losses

[0066] ξ is the local resistance coefficient;

[0067] V is the average flow velocity in the effective cross section;

[0068] g is the acceleration due to gravity;

[0069] In the original radial intake port scheme, when the fluid flows through the variable-section channel, it collides with the outer wall of the roller, and the size and direction of the falling body will change, causing collisions between the fluid and the fluid, and the fluid and the local structure, thereby generating vortices, which hinder the fluid scheme and increase local resistance; in the new beveled intake port scheme, the direction of the intake port can maintain a large degree of parallelism with the inner wall of the cylinder and the outer wall of the roller, and the degree of obstruction caused by the viscosity of the boundary layer and the vortex caused by the structure is smaller, because the pressure drop will be lower than that of the original radial intake port scheme.

[0070] According to the above test results, the beveled intake port has a better suction effect when the bevel angle range is 20-50 degrees. In this test, when the bevel angle exceeds 50 degrees and the bevel angle is larger, while maintaining the same cylinder intake port range (the same area A), the intake pipe will become very slender (the wet perimeter l becomes larger), and the equivalent diameter will become very small. The resistance along the way will increase Therefore, when the oblique air intake is larger, the flow resistance will be greater than that of the original radial air intake, which is consistent with the test results. The oblique angle refers to the angle between the extension direction of the air intake channel 5 and the extension direction of the slide slot 2.

[0071] The cylinder of the present application adopts an oblique intake channel 3, which can greatly shorten the distance from the intake port to the vane groove 2. Compared with the radial intake port of the existing cylinder, the opening angle and closing angle of the intake can be greatly reduced. The reduction of the intake opening angle can reduce the area of ​​the arc triangle formed by the outer wall of the roller, the inner wall of the cylinder structure 1 and the inner wall of the vane structure 5, reduce the circumferential leakage during the intake process, increase the working volume of the compressor, and improve the volumetric efficiency; the reduction of the intake closing angle can increase the volume of the intake crescent cavity, increase the intake volume of each single-cylinder operation, and improve the volumetric efficiency.

[0072] The suction chamber of this application is "P"-shaped, while the existing cylinder structure 1 is "Y"-shaped. That is, at the cylinder suction port of the existing cylinder structure 1, because the flow velocity of the suction flow channel is perpendicular to the roller wall, the compressed medium collides violently with the roller, changes its direction, and disperses to both sides. The right side of the figure is prone to form eddy currents, causing eddy current losses, converting kinetic energy into heat energy, increasing the suction temperature, and increasing the power consumption of the compressor. The beveled suction port used in this application allows the suction flow channel to be relatively parallel to the roller cut edge, that is, the direction of the working medium flow velocity at the suction port remains tangent to the outer wall of the roller, resulting in lower power consumption losses, which is better than the common radial suction port solution.

[0073] The present application also discloses some embodiments, in which the outer wall of the connecting pipe 4 is at least partially in contact with the inner wall of the intake channel 3. The connecting pipe 4, the vane, the cylinder vane slot 2, the upper flange 7 and the lower flange 8 form a closed pipeline. The compressed working medium enters from the intake channel 3, flows from the nominal right side of the vane slot 2 of the cylinder structure 1 to the left side through the connecting pipe 4, and reaches the intake chamber inside the cylinder structure 1 to perform compression and work movement. The connecting pipe 4 is arranged in the middle of the vane structure 5 to avoid the reciprocating interference of the vane with the connecting pipe 4 during the compression movement of the compressor. The structure is simple and easy to implement. The connecting pipe 4 is a thin-walled tubular structure. The outer shape can be a round tube, a square tube, or a special-shaped tube. It has an interference fit with the cylinder structure 1. There is an oblique cut on one side of the connecting pipe 4 to avoid interference contact with the inner side of the vane when the spring compression amount is minimum.

[0074] The pump assembly of the present application primarily comprises a cylinder with an intake passage 3, a vane structure 5 and a connecting pipe 4, upper and lower flanges 7 and 8, a crankshaft 9, and a roller structure 6. The vane structure 5 is provided with a through-hole 51, serving as a clearance hole for the connecting pipe 4. The connecting pipe 4 obliquely passes through the cylinder structure 1, the vane structure 5, and the cylinder structure 1. Compared to the related art method of slotting the cylinder structure 1 on one side, the present invention allows for the intake opening and closing angles to be closed earlier, which helps improve volumetric efficiency and increase working volume. The intake direction does not need to be changed, resulting in smoother intake and reduced intake losses. The contact area between the vane and the cylinder groove is reduced, which helps reduce friction and power consumption.

[0075] After the six parts of the pump body (crankshaft 9, roller structure 6, upper flange 7, lower flange 8, cylinder structure 1, and vane structure 5) are assembled, the connecting pipe 4 is pushed into the position of the cylinder's oblique intake channel 3 and pressure is applied to complete the tight fit. The assembly process is simple and quick.

[0076] According to an embodiment of the present application, a compressor is provided, including a pump body assembly, which is the above-mentioned pump body assembly.

[0077] According to an embodiment of the present application, an air conditioner is provided, including a compressor, which is the above-mentioned compressor.

[0078] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0079] The above are merely preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present application shall be included within the scope of protection of the present application. The above are merely preferred embodiments of the present application. It should be noted that those skilled in the art may make various improvements and variations without departing from the technical principles of the present application, and such improvements and variations shall also be considered within the scope of protection of the present application.

Claims

1. A pump assembly, characterized in that: The invention comprises a cylinder structure (1), wherein an air intake channel (3) is provided on the cylinder structure (1); the air intake channel (3) extends from the outer peripheral side of the cylinder structure (1) to the inner peripheral side of the cylinder structure (1), and the air intake channel (3) can guide gas from the outside of the cylinder structure (1) into the inside of the cylinder structure (1); and an angle is formed between the extension direction of the air intake channel (3) and the radial direction of the cylinder structure (1); The pump body assembly further comprises a connecting pipe (4) and a sliding vane structure (5), wherein the sliding vane structure (5) is movably arranged in the cylinder structure (1); the air intake channel (3) comprises a first section and a second section; The sliding structure (5) is provided with a through hole (51), and the through hole (51) is connected to the first section and the second section; the connecting pipe (4) is arranged in the through hole (51), and the connecting pipe (4) is connected to the first section and the second section; During the movement of the sliding structure (5), the position of the connecting pipe (4) remains unchanged; The cylinder structure (1) is further provided with a vane groove (2); the angle between the air intake channel (3) and a perpendicular line in the extending direction of the vane groove (2) is θ; 0.25≤|cosθ|<1.

2. The pump assembly according to claim 1, characterized in that: The vane groove (2) extends in the radial direction of the cylinder structure (1); and the air intake channel (3) extends from one circumferential side of the vane groove (2) to the other circumferential side of the vane groove (2).

3. The pump assembly according to claim 2, characterized in that: The vane structure (5) divides the interior of the cylinder structure (1) into an air intake chamber and an air discharge chamber; the first section is located on one circumferential side of the vane groove (2), and the second section is located on the other circumferential side of the vane groove (2).

4. The pump assembly according to claim 2, characterized in that: The first section extends from the slide groove (2) to the outer peripheral wall of the cylinder structure (1), and the cross-sectional area of ​​the first section gradually increases in a direction approaching the outer peripheral wall of the cylinder structure (1).

5. The pump assembly according to claim 3, characterized in that: The pump assembly further comprises a crankshaft (9), the eccentricity of the crankshaft (9) being e; the connecting pipe (4) extends from the first section through the through hole (51) to the second section; the connecting pipe (4) is provided with a necking section; or Wherein, s1 is the inlet cross-sectional area of ​​the connecting pipe (4), s2 is the cross-sectional area of ​​the necking section; s3 is the maximum cross-sectional area of ​​the outlet of the connecting pipe (4); h1 is the enthalpy value of the inlet cross-sectional area of ​​the connecting pipe (4); h2 is the enthalpy value of the minimum cross-sectional area of ​​the necking section of the connecting pipe (4); h3 is the enthalpy value of the outlet cross-sectional area of ​​the connecting pipe (4); ρ2 is the density of the minimum cross-sectional area of ​​the necking section of the connecting pipe (4); ρ3 is the density of the outlet cross-sectional area of ​​the connecting pipe (4), and the axial height of the cylinder structure (1) is h.

6. The pump assembly according to claim 2, characterized in that: The pump body assembly further comprises a crankshaft (9), the eccentricity of the crankshaft (9) being e; in the moving direction of the vane structure (5), the minimum length of the through hole (51) is L1; the minimum distance between the through hole (51) and the radial outer surface of the vane structure (5) is L2; ​​the inner diameter of the cylinder structure (1) is D, and the axial height of the cylinder structure (1) is h; the pump body assembly further comprises a roller structure (7), the outer diameter of the roller structure (7) being d; Among them, L1≥2e; and / or, and / or, 7. The pump assembly according to claim 4, characterized in that: in, The outer wall of the connecting pipe (4) is at least partially in contact with the inner wall of the air intake channel (3).

8. A compressor comprising a pump assembly, characterized in that: The pump body assembly is the pump body assembly according to any one of claims 1 to 7.

9. An air conditioner comprising a compressor, characterized in that: The compressor is the compressor described in claim 8.

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