WO2023231383A1 - 压缩机和空调器 - Google Patents

压缩机和空调器 Download PDF

Info

Publication number
WO2023231383A1
WO2023231383A1 PCT/CN2022/140632 CN2022140632W WO2023231383A1 WO 2023231383 A1 WO2023231383 A1 WO 2023231383A1 CN 2022140632 W CN2022140632 W CN 2022140632W WO 2023231383 A1 WO2023231383 A1 WO 2023231383A1
Authority
WO
WIPO (PCT)
Prior art keywords
mass
roller
center
crankshaft
axis
Prior art date
Application number
PCT/CN2022/140632
Other languages
English (en)
French (fr)
Inventor
董明珠
胡余生
胡远培
魏会军
杨欧翔
张心爱
Original Assignee
珠海格力电器股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2023231383A1 publication Critical patent/WO2023231383A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight

Definitions

  • the present disclosure relates to the technical field of compressors, and specifically to a compressor and an air conditioner.
  • Compressors have strict noise and vibration control requirements during the design process.
  • household air-conditioning compressors have stricter noise and vibration requirements. How to reduce the vibration level of the compressor has always been a research topic for compressor developers.
  • Household air conditioners often use rotary compressors.
  • the crankshaft is equipped with an eccentric part at the position of the cylinder.
  • the eccentric structure drives the rollers to operate, thereby realizing the suction, compression, and exhaust processes in the compressor.
  • a balance block is usually installed at the upper and lower ends of the motor to ensure the force and moment balance of the entire shaft system, thereby reducing vibration.
  • due to the relatively large mass of the main and auxiliary balance blocks it will cause the top of the crankshaft to have an eccentric part.
  • a compressor which includes:
  • crankshaft the crankshaft includes a first eccentric part and a second eccentric part, the first eccentric part and the second eccentric part are respectively located on different shaft segments of the crankshaft;
  • the first roller is sleeved on the outer periphery of the first eccentric part, and the interior of the first roller is a solid structure;
  • the second roller is sleeved on the outer periphery of the second eccentric part.
  • the second roller has a hollow part inside to form a cavity;
  • the motor rotor is sleeved on the crankshaft
  • the balance weight is only installed on one end of the motor rotor along the axial direction;
  • the center of mass of the first eccentric part and the first roller is the first center of mass
  • the axis of the first center of mass passes through the first center of mass and is parallel to the axis of the crankshaft
  • the center of mass of the second eccentric part and the second roller is the second center of mass
  • the axis of the second center of mass passes through the second center of mass and is parallel to the axis of the crankshaft
  • the center of mass of the balance weight, the axis of the first center of mass and the axis of the second center of mass are located in the same plane
  • the first center of mass is located on the first side of the axis of the crankshaft
  • the center of mass of the balance mass is located on the second side of the axis of the crankshaft, so that the axis of the crankshaft is located between the center of mass of the balance mass and the first center of mass
  • the second center of mass is located on The second side of the axis of the crankshaft.
  • the first roller is axially located between the motor rotor and the second roller.
  • the balance weight is disposed on the motor rotor and is located at an end away from the first roller along the axis of the crankshaft; or the balance weight is disposed on the motor rotor and is located near the first roller along the axis of the crankshaft. One end.
  • the hollow part is an annular cavity
  • the second roller is divided by the annular cavity into a radial inner wall, a radial outer wall, a first axial end and a second axial end
  • the radial thickness of the radial inner wall is b
  • the radial thickness of the radial outer wall is a
  • the axial thickness of the first axial end is c
  • the axial thickness of the second axial end is d
  • the second roller The total radial thickness of the second roller is t
  • the total axial thickness of the second roller is h, and the following relationships are satisfied:
  • the hollow portions include two, and the two hollow portions are spaced apart along the axial direction of the second roller, and have a support portion between the two hollow portions, and the radial inner walls of the two hollow portions have a radial diameter.
  • the axial thickness is b1
  • the radial thickness of the radial outer wall is a1
  • the axial thickness of the third axial end of one hollow part away from the other hollow part is c1
  • the axial thickness of the fourth axial end on one side of the hollow part is d1
  • the total radial thickness of the second roller is t
  • the total axial thickness of the second roller is h
  • the support portion has an axial thickness e1
  • the number of hollow portions is n, and the n hollow portions are sequentially spaced along the axial direction of the second roller, where n ⁇ 1; the total radial thickness of the second roller is t, and the total radial thickness of the second roller is t.
  • the total axial thickness is h;
  • the radial thickness of the radial outer walls of the n hollow parts is all a, and the radial thickness of the radial inner walls of the n hollow parts is a, and a ⁇ t/(2(n+1)), b ⁇ t /(2(n+1));
  • the axial thickness at one axial end of each hollow part is c, and the axial thickness at the other axial end of each hollow part is d, and c ⁇ h/(4(n+1 )), d ⁇ h/(4(n+1));
  • the axial thickness of the multiple support parts is equal to e, and e ⁇ h/(8(n+1)).
  • the compressor is a vertical compressor
  • the first roller and the second roller are arranged up and down
  • the first roller is located above the second roller
  • the motor rotor is located above the first roller
  • the balance The block is arranged on the upper end surface of the motor rotor or on the lower end surface of the motor rotor.
  • the mass of the first roller and the first eccentric part is m1
  • the minimum distance between the first center of mass and the axis of the crankshaft is r1
  • the mass of the second roller and the second eccentric part is m0
  • the second center of mass The minimum distance from the axis of the crankshaft is r0
  • the mass of the balance mass is m2
  • the minimum distance from the center of mass of the balance mass to the axis of the crankshaft is r2
  • the mass of the first roller and the first eccentric part is m1
  • the minimum distance between the first center of mass and the axis of the crankshaft is r1
  • the mass of the second roller and the second eccentric part is m0
  • the second center of mass The minimum distance from the axis of the crankshaft is r0
  • the mass of the balance mass is m2
  • the minimum distance from the center of mass of the balance mass to the axis of the crankshaft is r2
  • along the axis of the crankshaft there is a distance l1 between the first center of mass and the second center of mass
  • There is a distance l2 between the center of mass of the balance mass and the second center of mass and the following relationship exists:
  • the present disclosure also provides an air conditioner including the compressor of the above embodiment.
  • Figure 1 is a compressor structural diagram of related technology 1
  • Figure 2 is a compressor structural diagram of related technology 2
  • Figure 3 is a structural diagram of a compressor in related technology 3
  • Figure 4 is a compressor structural diagram of related technology 4.
  • Figure 5 is a cross-sectional view of the entire compressor of some embodiments of the low-vibration balancing system of the present disclosure
  • Figure 6 is a schematic diagram of the single pair balance weight balancing system of the present disclosure.
  • Figure 7 is a schematic structural diagram of some embodiments of the second roller of the present disclosure.
  • Figure 8 is a schematic diagram of the balancing system of the present disclosure.
  • Figure 9 is a technical effect diagram comparing the present disclosure with conventional solutions.
  • Figure 10 is a schematic diagram of a single main balance weight balancing system according to alternative embodiment 1 of the present disclosure.
  • Figure 11 is a schematic diagram of the second roller of the intermediate belt support portion of alternative embodiment 2 of the present disclosure.
  • 90A radial inner wall
  • 90B radial outer wall
  • 90C first axial end
  • 90D second axial end
  • 90E third axial end
  • 90F fourth axial end
  • the patent number CN201510737107.9 discloses a rotary compressor and a heat pump system with the same. As shown in Figure 1, it uses hollow rollers to reduce the mass of the eccentric component, thereby reducing the main balance weight. .
  • this technology is only for single-cylinder compressors and cannot completely eliminate the main balance weight to significantly reduce crankshaft deflection.
  • the patent number CN201910798100.6 discloses a crankshaft assembly, compressor and air conditioner. As shown in Figure 2, this technology makes the upper eccentric mass and upper roller mass greater than the lower eccentric and lower eccentric mass for the double-cylinder compressor structure. The quality of the rollers can thereby reduce the number of balance weights, significantly reducing crankshaft deflection and compressor vibration levels. However, this different structure of the upper and lower cylinders will cause a large loss of compressor performance, and will also make the processing technology more complex and the cost higher.
  • the patent number CN201811012300.6 discloses a two-cylinder rotary compressor and its crankshaft. As shown in Figure 3, this technology makes the upper eccentric mass and upper eccentric distance larger than the lower eccentric mass and By lowering the eccentricity, the number of balance weights can be reduced, and the deflection of the crankshaft and the vibration level of the compressor can be greatly reduced. However, reducing the mass of the eccentric part is very limited. According to the force and moment balance, it is not easy to design a single balance weight.
  • the patent number CN03144393.1 discloses a crankshaft of a rotary compressor, as shown in Figure 4.
  • This technology is provided with a crescent-shaped or arcuate groove for the eccentric part of the crankshaft, and the eccentric part is separate and can be opposite to the crankshaft. Rotate so that the center of gravity of the eccentric part coincides with the center of gravity of the crankshaft, thus eliminating the need for a balance weight.
  • this technology does not consider the impact of vibration caused by roller eccentricity and the impact of gas force caused by gas compression. Obviously, large vibration will still occur without using a balance weight.
  • compressors in the related art have technical problems such as vibration and noise levels worsening at high frequencies, which are especially serious for high-speed compressors, this disclosure researches and designs a compressor and an air conditioner.
  • the technical problem to be solved by the present disclosure is to overcome the shortcoming of the compressor in the prior art that the vibration damping effect is poor, especially at high frequencies, thereby providing a compressor and an air conditioner.
  • the present disclosure can reduce the total mass of the second roller and the second eccentric part by making one of the rollers in the double-cylinder or multi-cylinder compressor into a hollow structure, and make the second center of mass face the direction of the crankshaft. Close to or located on the axis of the crankshaft, under the action of the first roller, the first eccentric part and the balance mass, the second roller, the second eccentric part, the first roller, the first eccentric part and the balance mass can reach The balance of force and torque can effectively remove the balance block that usually needs to be installed at the other end of the motor rotor axis. Due to the reduction of the number and quality of the balance block, the deflection of the crankshaft is greatly reduced, and the vibration and noise level of the compressor are reduced.
  • the centrifugal force of the second eccentric part and the second roller becomes smaller, thereby reducing the contact stress corresponding to the contact position between the crankshaft and the flange, effectively improving the reliability of the compressor;
  • the roller becomes lighter, which reduces the friction power consumption between the roller and the flange, the intermediate partition plate, the cylinder, etc., so it can also effectively reduce the motor drive power consumption and improve energy efficiency;
  • the present disclosure reduces the number and weight of the balance weight, and The weight of the lower roller is reduced, which solves the problem of heavy weight of the compressor with double balance blocks and solid rollers in the existing balance system, effectively reducing the weight of the entire machine and saving costs.
  • a compressor for example, a two-cylinder rolling rotor compressor
  • the crankshaft 2 includes a first eccentric part 20 and a second eccentric part 21.
  • the first eccentric part 20 and the second eccentric part 21 are respectively located on different shaft segments of the crankshaft 2.
  • the first roller 6 is sleeved on
  • the second roller 9 is sleeved on the outer periphery of the first eccentric part 20 and the second eccentric part 21;
  • the first roller 6 has a solid structure inside, and the second roller 9 has a hollow portion 90 inside, forming a cavity.
  • the motor rotor 3 is sleeved on the crankshaft 2.
  • the crankshaft 2 includes a main shaft body 22.
  • the motor rotor 3 is sleeved on the first end of the main shaft body 22.
  • the first eccentric part 20 and the second eccentric part 21 are located on the first end of the main shaft body 22. Two ends.
  • the balance weight 1 is provided at one axial end of the motor rotor 3, and no balance weight is provided at the other axial end of the motor rotor 3;
  • the center of mass of the first eccentric part 20 and the first roller 6 is the first center of mass.
  • the axis of the first center of mass passes through the first center of mass and is parallel to the axis of the crankshaft 2.
  • the center of mass of the second eccentric part 21 and the second roller 9 is the first center of mass.
  • Two centers of mass, the axis of the second center of mass passes through the second center of mass and is parallel to the axis of the crankshaft 2, and the center of mass of the balance weight 1, the axis of the first center of mass and the axis of the second center of mass are located in the same plane, which plane passes through the axis of the crankshaft 2 ;
  • the first center of mass is located on the first side of the axis of the crankshaft 2
  • the center of mass of the balance weight 1 is located on the second side of the axis of the crankshaft 2, so that the axis of the crankshaft is located between the center of mass of the balance mass 1 and the first center of mass
  • the second center of mass is located on the second side of the axis of the crankshaft 2 .
  • the present disclosure can reduce the total mass of the second roller 9 and the second eccentric portion 21 by making one of the rollers in the double-cylinder or multi-cylinder compressor into a hollow structure, and make the second center of mass toward the crankshaft.
  • the direction is close to or located on the axis of the crankshaft 2.
  • the first eccentric part 20 and the balance weight 1, the second roller 9, the second eccentric part 21, the first roller 6 can be , the first eccentric part 20 and the balance weight 1 achieve a balance of forces and moments, thereby effectively removing the balance weight 1 that usually needs to be installed at the other axial end of the motor rotor 3, due to the reduction in the quantity and quality of the balance weight 1 , greatly reducing the crankshaft deflection, reducing compressor vibration and noise levels; and due to the reduced weight of the rollers, the centrifugal force of the second eccentric part 21 and the second roller 9 becomes smaller, corresponding to the contact between the crankshaft 2 and the flange The contact stress at the position is reduced, which effectively improves the reliability of the compressor; because the rollers become lighter, the friction power consumption between the rollers and the flange, the intermediate partition plate and the cylinder is reduced, so it can also effectively reduce the motor drive Power consumption and improved energy efficiency; this disclosure reduces the number and weight of the balance weight 1 and reduces the weight of the second roller 9, thus
  • the balancing system applied to a double-cylinder rolling rotor compressor 100 includes: balance weight 1, crankshaft 2, first roller 6 (upper roller), second roller It is composed of roller 9 (lower roller).
  • the crankshaft 2 is provided with a first eccentric part 20 (upper eccentric part) and a second eccentric part 21 (lower eccentric part).
  • the first roller 6 is sleeved on the first eccentric part 20 of the crankshaft 2 and placed on the upper cylinder.
  • the upper end surfaces of the upper cylinder 7 and the first roller 6 are in contact with the lower end surface of the upper flange 5, the lower end surfaces of the upper cylinder 7 and the first roller 6 are in contact with the upper end surface of the partition 8, and the second roller 9 is sleeved on the second eccentric part 21 of the crankshaft 2 and placed in the inner cavity of the lower cylinder 10.
  • the upper end surfaces of the lower cylinder 10 and the second roller 9 are in contact with the lower end surface of the partition plate 8.
  • the lower cylinder 10 and the second roller 9 are in contact with each other.
  • the lower end surface of the roller 9 is in contact with the upper end surface of the lower flange 11, in which the upper flange 5, the upper cylinder 7, the partition 8, the lower cylinder 10 and the lower flange 11 are directly locked through screws.
  • the long shaft section of the crankshaft 2 passes through the inner hole of the upper flange 5
  • the intermediate shaft section of the crankshaft 2 passes through the inner hole of the partition 8
  • the short shaft section of the crankshaft 2 passes through the inner hole of the lower flange 11 .
  • the long axis of the crankshaft 2 and the inner hole of the motor rotor 3 are connected through an interference fit.
  • the rotation of the motor rotor 3 drives the crankshaft 2 to rotate.
  • the first eccentric part 20 and the second eccentric part 21 of the crankshaft 2 drive the first roller 6 and the first roller 6 respectively.
  • the second roller 9 rotates in the upper cylinder 7 and the lower cylinder 10 .
  • a balance block 1 is provided at the upper end of the motor rotor 3 and is connected to the motor rotor 3 through rivets 4 to maintain the balance of the entire balance system.
  • the inner diameter and cylinder height of the upper cylinder 7 and the lower cylinder 10 are set to the same, the inner and outer diameters and heights of the first roller 6 and the second roller 9 are both set to the same, and the inner and outer diameters and heights of the first roller 6 and the second roller 9 are set to the same.
  • the first eccentric part 20 and the second eccentric part 21 have the same structure and are arranged on both sides of the crankshaft 2 with a phase difference of 180°.
  • the overall structure and size of the upper and lower chambers remain the same and the rollers are arranged with a phase difference of 180°, so that the crankshaft 2 can withstand more stress.
  • the balance weight 1 is located on the side of the lower eccentric part of the crankshaft 2, and its center of mass is located in the plane of the mass center axes of the upper and lower eccentric parts of the crankshaft 2.
  • Figure 6 is a schematic diagram of a single pair of balance weight balancing system.
  • the first roller 6 sleeved on the first eccentric part 20 of the crankshaft 2 is a solid structure
  • the second roller 9 has a hollow structure.
  • the first roller 6 and the second roller 9 are made of the same material.
  • the hollow portion 90 of the second roller 9 reduces weight compared with the first roller 6. Since the first roller 6 and the second roller 9 are The second roller 9 has poor quality.
  • a balance block 1 must be installed on the motor on one side of the second roller 9. The structure, height, weight, center of mass distance, etc.
  • the balance mass 1 in the present disclosure can be designed to have a smaller mass, and the height of the balance mass 1 can be lower, which can not only greatly reduce the deflection of the top of the crankshaft 2 and reduce the vibration of the compressor, but also greatly reduce the vibration of the balance mass 1 during rotation. The resulting wind resistance power consumption improves compressor energy efficiency.
  • Figure 9 is a comparison of the technical effects of the disclosed solution and the conventional two-cylinder compressor solution.
  • the conventional solution adopts a balancing solution in which the upper and lower rollers are completely consistent and use two main and auxiliary balance weights.
  • the black rectangular block in Figure 9 represents the conventional solution, and the white rectangular block represents the disclosed solution.
  • the disclosed solution can reduce the maximum deflection of the crankshaft by 71% and the maximum contact stress of the crankshaft by 25%. It not only greatly reduces the compression It can also reduce the vibration level of the machine, reduce the wear between the crankshaft and the flange, and improve the reliability of parts.
  • the mass of the lower roller of the present disclosure is smaller than that of the upper roller.
  • the lower roller can be a hollow structure, a hollow structure with supports, or use lightweight materials;
  • the thickness of the radial inner wall 90A and the thickness of the radial outer wall 90B of the second roller 9 should satisfy the following relationship:
  • the thickness of the first axial end portion 90C located above and the thickness of the second axial end portion 90D located below the second roller 9 should satisfy the following relationship:
  • balance mass 1 there is only one balance mass 1 above and below the motor rotor 3.
  • the balance mass 1 can be located above or below the motor rotor 3.
  • the balance mass 1 is located on the side of the second eccentric portion 21 below the crankshaft 2, and
  • the center of mass is located in the plane of the mass center axis of the first eccentric part 20 and the second eccentric part 21 of the crankshaft 2;
  • the balance weight 1 has a flat structure and is fixed above or below the motor rotor 3 by rivets.
  • the balance block of the balance system has large volume and mass, large wind resistance, and large motor drive power consumption
  • the first roller 6 is located between the motor rotor 3 and the second roller 9 , and the second roller 9 is farther away from the motor rotor 3 relative to the first roller 6 .
  • the balance mass 1 is disposed on the motor rotor 3 and is located along the axis of the crankshaft 2 at one axial end away from the first roller 6; or, the balance mass 1 is disposed on the motor rotor 3 and along the axis of the crankshaft 2 The axis of is located close to the other axial end of the first roller 6.
  • the balance weight 1 is disposed along the axis of the crankshaft 2 at an end of the motor rotor 3 away from the first roller 6; in the alternative embodiment 1 shown in Figure 10, the balance weight 1 is arranged along the axis of the crankshaft 2.
  • the axis of the crankshaft 2 is disposed at one end of the motor rotor 3 close to the first roller 6 .
  • the balance weight 1 can also be arranged with the motor rotor 3 At the lower position, use it as the main balance weight and remove the auxiliary balance weight.
  • This solution can make the deflection of the top of the crankshaft 2 smaller, but it may cause the maximum deflection of the crankshaft to occur at the upper eccentric part (first eccentric part 20). This It is necessary to evaluate the influence of the crankshaft deformation on the operation of the upper roller in the upper cylinder 7. If the deflection of the crankshaft 2 at the upper eccentric part (first eccentric part 20) is too large, it may cause problems such as jamming or leakage of the roller and the cylinder. However, if the crankshaft deformation is still within the acceptable range, this solution will have a better vibration level than the single pair of balance weight solutions.
  • the hollow portion 90 there is one hollow portion 90 and the hollow portion 90 is an annular cavity.
  • the second roller is divided by the annular cavity into a radial inner wall 90A, a radial outer wall 90B, a first axial end portion 90C and a second roller.
  • the radial thickness of the radial inner wall 90A is b
  • the radial thickness of the radial outer wall 90B is a
  • the axial thickness of the first axial end 90C is c
  • the radial thickness of the second axial end 90D is The axial thickness is d
  • the total radial thickness of the second roller 9 is t
  • the total axial thickness of the second roller 9 is h, and the following relationships are satisfied:
  • FIG. 7 is a schematic diagram of the second roller 9 of the present disclosure having a hollow structure.
  • the second roller 9 is located below, its inner wall surface 91 is in contact with the second eccentric portion 21 of the crankshaft 2 , and its upper end surface 92 is in contact with the lower end surface of the partition 8
  • the inner wall surface 91 is provided with first chamfers 93 and second chamfers 94 up and down; the design of the hollow portion 90 determines the radial thickness a of the radial outer wall 90B, the radial thickness b of the radial inner wall 90A, the first axis Regarding the dimensions of the axial thickness c of the end 90C and the axial thickness d of the second axial end 90D, since the second roller 9 is located in the cylinder, when the refrigerant is compressed, both the inner and outer circles of the rollers will bear a larger load.
  • the radial thickness a of the radial outer wall 90B and the radial thickness b of the radial inner wall 90A should not be too thin, otherwise the inner and outer walls will be dented toward the middle, which will lead to leakage of refrigerant from the high-pressure chamber to the low-pressure chamber and rollers, slides, etc.
  • the inner and outer wall thickness of the second roller 9 should satisfy the following relationship:
  • the upper and lower end surfaces of the second roller 9 also have high oil film pressure, so the axial thickness c of the second axial end 90D and the axial thickness d of the second axial end 90D should not be too thin, otherwise it will cause
  • the upper and lower walls are dented inward, which in turn causes the refrigerant to leak from the end face of the second roller 9 and the parts of the second roller 9, the lower flange 11 and the partition 8 to wear.
  • the two hollow portions 90 there are two hollow portions 90 , and the two hollow portions 90 are spaced apart along the axial direction of the second roller 9 , and there is a support portion 95 between the two hollow portions 90 .
  • the two hollow portions 90 The radial thickness of the radial inner wall 90A of the two hollow parts 90 is both b1, the radial thickness of the radial outer wall 90B of the two hollow parts 90 is a1, and the third axial direction of one hollow part 90 away from the other hollow part 90
  • the axial thickness of the end 90E is c1
  • the axial thickness of the fourth axial end 90F of the other hollow part 90 on the side away from one hollow part 90 is d1
  • the total radial thickness of the second roller 9 is t.
  • the total axial thickness of the second roller 9 is h, and satisfies the following relationship:
  • the support portion 95 has an axial thickness e1 and has:
  • the second roller 9 can also be made into a structure with a hollow portion and a support portion 95. This can reduce the deformation of the inner and outer walls of the second roller 9 to a greater extent and prevent the roller from deforming. Problems such as refrigerant leakage and parts wear.
  • the thickness of the support portion 95 should satisfy the following relationship: Due to the support structure, the upper, lower, left and right wall thicknesses of the second roller 9 can satisfy the following relationship: The original hollow roller solution has a reasonable structure and will not produce large deformation.
  • This alternative embodiment can reduce the deformation to a greater extent, but will increase the processing cost accordingly, so it is more suitable for applications where the deformation amount of the hollow roller is required to be higher. High compressor.
  • the number of hollow parts is n, and the n hollow parts 90 are sequentially spaced along the axial direction of the second roller 9, where n ⁇ 1; the total radial thickness of the second roller 9 is t, and the The total axial thickness of the two rollers 9 is h;
  • the radial thickness of the radial outer walls 90B of the n hollow portions 90 is all a, and the radial thickness of the radial inner walls 90A of the n hollow portions 90 is a, and a ⁇ t/(2(n+1)) , b ⁇ t/(2(n+1));
  • each hollow portion 90 the axial thickness at one axial end of each hollow portion 90 is c, and the axial thickness at the other axial end of each hollow portion 90 is d, and c ⁇ h/(4( n+1)), d ⁇ h/(4(n+1));
  • the axial thickness of the multiple support portions 95 is equal to e, and e ⁇ h/(8(n+1)).
  • This alternative embodiment can reduce deformation to a greater extent, but will increase the processing cost accordingly. Therefore, it is more suitable for compression that requires higher deformation of hollow rollers. machine.
  • the compressor is a vertical compressor
  • the first roller 6 and the second roller 9 are arranged up and down
  • the first roller 6 is located above the second roller 9
  • the motor rotor 3 is located on the first roller.
  • the balance weight 1 is arranged on the upper end surface of the motor rotor 3 or on the lower end surface of the motor rotor 3 .
  • the mass of the first roller 6 and the first eccentric part 20 is m1
  • the minimum distance between the first center of mass and the axis of the crankshaft is r1
  • the mass of the second roller 9 and the second eccentric part 21 is m0.
  • the minimum distance between the second center of mass and the axis of the crankshaft is r0
  • the mass of the balance mass 1 is m2
  • the minimum distance between the center of mass of the balance mass 1 and the axis of the crankshaft is r2
  • FIG. 8 is a schematic diagram of the structural dimensions of the balance system of the present disclosure.
  • the upper eccentricity r1 is equal to the lower eccentricity r0. Since there is a difference in the upper and lower eccentric masses, a balance block 1 needs to be installed on the upper part of the motor rotor 3. In order to make the entire balance system have a smaller The deflection of the crankshaft needs to meet the force balance and moment balance schemes, and based on research experience, there is the following relationship between the mass, eccentricity and distance of the upper and lower rollers and balance blocks:
  • the mass of the first roller 6 and the first eccentric part 20 is m1
  • the minimum distance between the first center of mass and the axis of the crankshaft is r1
  • the mass of the second roller 9 and the second eccentric part 21 is m0.
  • the minimum distance between the second center of mass and the axis of the crankshaft is r0
  • the mass of the balance mass 1 is m2
  • the minimum distance between the center of mass of the balance mass 1 and the axis of the crankshaft is r2
  • along the axis direction of the crankshaft 2 the first center of mass and the second
  • the present disclosure also provides an air conditioner, which includes the compressor of the preceding item.
  • the lower roller can not only achieve the quality difference between the upper and lower rollers through hollowing, but also use different roller materials to achieve this function.
  • the upper roller still uses cast iron materials such as traditional FC300
  • the lower roller can still use cast iron materials such as traditional FC300.
  • the rollers are made of lighter materials, such as ceramics, aluminum alloys, titanium alloys and other lightweight materials. The quality difference is achieved through the density difference between the upper and lower rollers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

一种压缩机和空调器，压缩机包括曲轴（2）、第一滚子（6）、第二滚子（9）、电机转子（3）和平衡块（1）；第一滚子（6）的内部为实心结构，第二滚子（9）的内部具有空心部（90），平衡块（1）设置于电机转子（3）的轴向一端，电机转子（3）的轴向另一端不设置平衡块；第一偏心部（20）和第一滚子（6）的质心为第一质心，第一质心的轴线经过第一质心且与曲轴（2）的轴线平行，第二偏心部（21）和第二滚子（9）的质心为第二质心，第二质心的轴线经过第二质心且与所述曲轴（2）的轴线平行；平衡块（1）的质心、第一质心的轴线和第二质心的轴线位于同一平面内；在平面内，第一质心位于曲轴（2）的轴线的第一侧，平衡块（1）的质心位于曲轴（2）的轴线的第二侧，使得曲轴（2）的轴线位于平衡块（1）的质心与第一质心之间，第二质心位于曲轴（2）的轴线的第二侧。该结构能够减少平衡块数量及质量，降低曲轴挠度，减小压缩机振动和噪音水平；减小曲轴和法兰的接触应力，减小电机驱动耗功，提高能效；降低了整机重量。

Description

压缩机和空调器
相关申请的横向引用
本公开是以申请号为 202210603409.7，申请日为 2022年5月30日的中国申请为基础，并主张其优先权，该中国申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及压缩机技术领域，具体涉及一种压缩机和空调器。
背景技术
压缩机在设计过程中对噪音振动有严格的控制要求，尤其是家用空调用压缩机对噪音振动的要求更为严格，如何降低压缩机的振动水平一直是压缩机开发人员研究的课题。家用空调常采用转子压缩机，曲轴在气缸位置处设置有偏心部，通过偏心结构带动滚子运转，进而实现压缩机内的吸气、压缩、排气过程。由于曲轴设置有偏心部，通常在电机上下端各设置一个平衡块来保证整个轴系的受力和力矩平衡，进而减小振动，但由于主副平衡块质量相对较大，会引起曲轴顶端有较大的挠度变形，并结合电机转子的高速运作，使得压缩机依然会有较大的振动。随着压缩机向高速小型化发展，压缩机的振动问题越来越严峻，急需开发一种新的平衡系统来大幅降低压缩机的振动。
发明内容
为了解决上述问题，本公开提供一种压缩机，其包括：
曲轴，曲轴包括第一偏心部和第二偏心部，第一偏心部和第二偏心部分别位于曲轴的不同的轴段上；
第一滚子，套设于第一偏心部的外周，第一滚子的内部为实心结构；
第二滚子，套设于第二偏心部的外周，第二滚子的内部具有空心部，形成空腔；
电机转子，套设于曲轴；和
平衡块，仅设置于电机转子沿轴向一端；
其中，第一偏心部和第一滚子的质心为第一质心，第一质心的轴线经过第一质心且与曲轴的轴线平行，第二偏心部和第二滚子的质心为第二质心，第二质心的轴线经过第二 质心且与曲轴的轴线平行，且平衡块的质心、第一质心的轴线和第二质心的轴线位于同一平面内；
并且在平面内，第一质心位于曲轴的轴线的第一侧，平衡块的质心位于曲轴的轴线的第二侧，使得曲轴的轴线位于平衡块的质心与第一质心之间，第二质心位于曲轴的轴线的第二侧。
在一些实施方式中，第一滚子沿轴向位于电机转子与第二滚子之间。
在一些实施方式中，平衡块设置于电机转子上，且沿曲轴的轴线位于远离第一滚子的一端；或者，平衡块设置于电机转子上，且沿曲轴的轴线位于靠近第一滚子的一端。
在一些实施方式中，空心部为一个，空心部为环形空腔，第二滚子被环形空腔分隔成径向内壁、径向外壁、第一轴向端部和第二轴向端部，径向内壁的径向厚度为b，径向外壁的径向厚度为a，第一轴向端部的轴向厚度为c，第二轴向端部的轴向厚度为d，第二滚子的径向总厚度为t，第二滚子的轴向总厚度为h，并满足下列关系：
Figure PCTCN2022140632-appb-000001
Figure PCTCN2022140632-appb-000002
在一些实施方式中，空心部包括两个，且两个空心部沿第二滚子的轴向间隔设置，且在两个空心部之间具有支撑部，两个空心部的径向内壁的径向厚度均为b1，径向外壁的径向厚度均为a1，其中一个空心部的远离另一个空心部一侧的第三轴向端部的轴向厚度为c1，另一个空心部的远离一个空心部一侧的第四轴向端部的轴向厚度为d1，第二滚子的径向总厚度为t，第二滚子的轴向总厚度为h，并满足下列关系：
Figure PCTCN2022140632-appb-000003
Figure PCTCN2022140632-appb-000004
在一些实施方式中，支撑部的轴向厚度为e1，并且
Figure PCTCN2022140632-appb-000005
在一些实施方式中，空心部个数为n，n个空心部依次沿第二滚子的轴向间隔设置，其中n≥1；第二滚子的径向总厚度为t，第二滚子的轴向总厚度为h；
n个空心部的径向外壁的径向厚度均为a，n个空心部的径向内壁的径向厚度均为a，并有a≥t/(2(n+1))，b≥t/(2(n+1))；
n个空心部中，每个空心部的轴向一端的轴向厚度为c，且每个空心部的轴向另一端的轴向厚度为d，并有c≥h/(4(n+1))，d≥h/(4(n+1))；
n个空心部中相邻两个空心部之间具有支撑部，多个支撑部的轴向厚度均相等且为e，并有e≥h/(8(n+1))。
在一些实施方式中，压缩机为立式压缩机，第一滚子和第二滚子上下布置，且第一滚子位于第二滚子的上方，电机转子位于第一滚子的上方，平衡块设置于电机转子的上端面或设置于电机转子的下端面。
在一些实施方式中，第一滚子和第一偏心部的质量为m1，第一质心距离曲轴的轴线的最小距离为r1，第二滚子和第二偏心部的质量为m0，第二质心距离曲轴的轴线的最小距离为r0，平衡块的质量为m2，平衡块的质心距离曲轴的轴线的最小距离为r2，并满足下列关系：
Figure PCTCN2022140632-appb-000006
在一些实施方式中，第一滚子和第一偏心部的质量为m1，第一质心距离曲轴的轴线的最小距离为r1，第二滚子和第二偏心部的质量为m0，第二质心距离曲轴的轴线的最小距离为r0，平衡块的质量为m2，平衡块的质心距离曲轴的轴线的最小距离为r2，沿曲轴的轴线方向，第一质心与第二质心之间存在距离l1，平衡块的质心与第二质心之间存在距离l2，存在如下关系：
Figure PCTCN2022140632-appb-000007
本公开还提供一种空调器，其包括上述实施例的压缩机。
附图说明
图1为相关技术1的压缩机结构图；
图2为相关技术2的压缩机结构图；
图3为相关技术3的压缩机结构图；
图4为相关技术4的压缩机结构图；
图5是本公开的低振动平衡系统的压缩机的一些实施例的整机剖面图；
图6是本公开的单副平衡块平衡系统示意图；
图7是本公开的第二滚子的一些实施例的结构示意图；
图8是本公开的平衡系统示意图；
图9是本公开与常规方案相比的技术效果图；
图10是本公开替代实施例1的单主平衡块平衡系统示意图；
图11是本公开替代实施例2的中间带支撑部的第二滚子示意图。
附图标记表示为：
1、平衡块；2、曲轴；3、电机转子；4、铆钉；5、上法兰；6、第一滚子；7、上气缸；8、隔板；9、第二滚子；10、下气缸；11、下法兰；20、第一偏心部；21、 第二偏心部；22、主轴体；90、空心部；100、压缩机。
90A、径向内壁；90B、径向外壁；90C、第一轴向端部；90D、第二轴向端部；90E、第三轴向端部；90F、第四轴向端部；
91、内壁面；92、上端面；93、第一倒角；94、第二倒角；95、支撑部。
具体实施方式
为使本公开的目的、技术方案和优点更加清楚，下面将结合本公开具体实施例及相应的附图对本公开技术方案进行清楚、完整地描述。显然，所描述的实施例仅是本公开一部分实施例，而不是全部的实施例。基于本公开中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
专利号为CN201510737107.9的专利公开了一种旋转式压缩机及具有其的热泵系统，如图1所示，其采用空心滚子来减小偏心组件的质量，进而可减少主平衡块配重。但是这种技术仅针对单缸压缩机，且并不能完全取消主平衡块进而大幅降低曲轴挠度。
专利号为CN201910798100.6的专利公开了一种曲轴组件、压缩机和空调器，如图2所示，该技术针对双缸压缩机结构使得上偏心质量和上滚子质量均大于下偏心和下滚子质量，进而可以减少平衡块数量，大幅降低曲轴挠度及压缩机振动水平。但是这种上下气缸不同的结构会造成压缩机性能的较大损失，且会造成加工工艺更加复杂，成本更高。
专利号为CN201811012300.6的专利公开了一种双缸旋转式压缩机及其曲轴，如图3所示，该技术针对双缸压缩机结构使得上偏心质量和上偏心距均大于下偏心质量和下偏心距，进而可以减少平衡块数量，大幅降低曲轴挠度及压缩机振动水平，但是减小偏心部质量非常有限，根据受力和力矩平衡，并不易设计出单个平衡块。
专利号为CN03144393.1的专利公开了一种旋转式压缩机的曲轴，如图4所示，该技术针对曲轴偏心部设置月牙型或弓型凹槽，并且偏心部为分离式与曲轴可相对转动，使得偏心部的重心和曲轴重心重合，进而省去平衡块。但是该技术并未考虑滚子偏心带来的振动影响以及气体压缩时带来的气体力的影响，显然不采用平衡块依然会有较大的振动产生。
由于相关技术中的压缩机存在高频下振动和噪音水平加剧恶化，尤其对于高速压缩机更为严重等技术问题，因此本公开研究设计出一种压缩机和空调器。
因此，本公开要解决的技术问题在于克服现有技术中的压缩机存在尤其在高频下减振效果不佳的缺陷，从而提供一种压缩机和空调器。
本公开提供的一种压缩机和空调器具有如下有益效果：
本公开通过将双缸或多缸压缩机中的其中一个滚子做成空心的结构形式，能够减小第二滚子和第二偏心部的总质量，并且使得第二质心朝着曲轴的方向靠近或位于曲轴的轴线上，在第一滚子、第一偏心部和平衡块的作用下，能够使得第二滚子、第二偏心部、第一滚子、第一偏心部和平衡块达到力的平衡，以及力矩的平衡，从而能够有效地去除掉电机转子轴向另一端通常需要设置的平衡块，由于减少了平衡块数量及质量，大幅降低曲轴挠度，减小压缩机振动和噪音水平；并且由于滚子的重量减小，使得第二偏心部和第二滚子的离心力变小，从而对应到曲轴和法兰接触位置的接触应力减小，有效提高了压缩机的可靠性；由于滚子变轻，使得滚子与法兰、中间隔板以及气缸等的摩擦功耗减小，因此还能够有效减小电机驱动耗功，提高能效；本公开由于减少平衡块数量及重量，并且减轻了下滚子的重量，解决了现有的平衡系统双平衡块及实心滚子的压缩机重量重的问题，有效降低了整机重量，节省了成本。
结合图5-11所示，本公开实施例提供了一种压缩机(例如，双缸滚动转子压缩机)，其包括：曲轴2、第一滚子6、第二滚子9、电机转子3和平衡块1，曲轴2包括第一偏心部20和第二偏心部21，第一偏心部20和第二偏心部21分别位于曲轴2的不同的轴段上，第一滚子6套设于第一偏心部20的外周，第二滚子9套设于第二偏心部21的外周；
第一滚子6的内部为实心结构，第二滚子9的内部具有空心部90，形成空腔。电机转子3套设于曲轴2，具体地，曲轴2包括主轴体22，电机转子3套设于主轴体22的第一端，第一偏心部20和第二偏心部21位于主轴体22的第二端。平衡块1设置于电机转子3的轴向一端，电机转子3的轴向另一端不设置平衡块；
第一偏心部20和第一滚子6的质心为第一质心，第一质心的轴线经过第一质心且与曲轴2的轴线平行，第二偏心部21和第二滚子9的质心为第二质心，第二质心的轴线经过第二质心且与曲轴2的轴线平行，且平衡块1的质心、第一质心的轴线和第二质心的轴线位于同一平面内，该平面通过曲轴2的轴线；
并且在平面内，第一质心位于曲轴2的轴线的第一侧，平衡块1的质心位于曲轴2的轴线的第二侧，使得曲轴的轴线位于平衡块1的质心与第一质心之间，第二质心位于曲轴2的轴线的第二侧。
本公开通过将双缸或多缸压缩机中的其中一个滚子做成空心的结构形式，能够减小 第二滚子9和第二偏心部21的总质量，并且使得第二质心朝着曲轴的方向靠近或位于曲轴2的轴线上，在第一滚子6、第一偏心部20和平衡块1的作用下，能够使得第二滚子9、第二偏心部21、第一滚子6、第一偏心部20和平衡块1达到力的平衡，以及力矩的平衡，从而能够有效地去除掉电机转子3轴向另一端通常需要设置的平衡块1，由于减少了平衡块1数量及质量，大幅降低曲轴挠度，减小压缩机振动和噪音水平；并且由于滚子的重量减小，使得第二偏心部21和第二滚子9的离心力变小，从而对应到曲轴2和法兰接触位置的接触应力减小，有效提高了压缩机的可靠性；由于滚子变轻，使得滚子与法兰、中间隔板以及气缸等的摩擦功耗减小，因此还能够有效减小电机驱动耗功，提高能效；本公开由于减少平衡块1数量及重量，并且减轻了第二滚子9的重量，解决了现有的平衡系统双平衡块及实心滚子的压缩机重量重的问题，有效降低了整机重量，节省了成本。
如图5所示，根据本申请的实施例，应用于一种双缸滚动转子压缩机100上的平衡系统包括：平衡块1、曲轴2、第一滚子6(上滚子)、第二滚子9(下滚子)组成。曲轴2上设有第一偏心部20(上偏心部)和第二偏心部21(下偏心部)，第一滚子6套设在曲轴2的第一偏心部20上，并放置于上气缸7内腔中，上气缸7和第一滚子6的上端面与上法兰5下端面接触，上气缸7和第一滚子6的下端面与隔板8上端面接触，第二滚子9套设在曲轴2的第二偏心部21上，并放置于下气缸10内腔中，下气缸10和第二滚子9的上端面与隔板8下端面接触，下气缸10和第二滚子9的下端面与下法兰11上端面接触，其中，上法兰5、上气缸7、隔板8、下气缸10和下法兰11直接通过螺钉进行锁合。曲轴2长轴段穿过上法兰5内孔，曲轴2中间轴段穿过隔板8内孔，曲轴2短轴段穿过下法兰11内孔。曲轴2长轴与电机转子3内孔通过过盈配合进行连接，电机转子3的转动带动曲轴2进行旋转，曲轴2的第一偏心部20和第二偏心部21分别带动第一滚子6和第二滚子9在上气缸7和下气缸10内进行旋转。电机转子3上端设置有平衡块1，并通过铆钉4连接在电机转子3上，以此来维持整个平衡系统的平衡。
为保证压缩机100的性能，上气缸7和下气缸10内部直径和缸高设置为相同，第一滚子6和第二滚子9的内外圆直径及高度均设置为相同，曲轴2的第一偏心部20和第二偏心部21结构相同且呈180°相位差分别设置在曲轴2两侧，上下腔的整体结构和尺寸保持一直且滚子呈180°相位差设置可以使曲轴2承受更均衡的力，来提高压缩机的性能。平衡块1位于曲轴2的下偏心部一侧，且质心位于曲轴2的上偏心部和下偏心部质心轴线的平面内。
图6为单副平衡块平衡系统示意图，在该系统中套设在曲轴2的第一偏心部20上的 第一滚子6为实心结构，套设在曲轴2的第二偏心部21上的第二滚子9为空心结构，第一滚子6和第二滚子9采用相同材料，第二滚子9的空心部90较第一滚子6减少了重量，由于第一滚子6和第二滚子9存在质量差，为保证压缩机受力平衡需在第二滚子9一侧电机上设置平衡块1，平衡块1的结构、高度、重量、质心距离等均可通过整个平衡系统的受力平衡和力矩平衡进行调节，由于平衡块1的质量由第一滚子6和第二滚子9的质量差所决定，故相较于传统的设置主副两个平衡块结构，本公开中的平衡块1可以设计的质量较小，且平衡块1高度可以更低，进而不仅可以大幅降低曲轴2顶端挠度减小压缩机振动，还可以大幅降低平衡块1在旋转过程中带来的风阻功耗提升压缩机能效。
图9为本公开方案与常规双缸压缩机方案的技术效果对比，常规方案采用上下滚子完全一致且使用主副两个平衡块的平衡方案。图9中的黑色矩形块表示常规方案，白色矩形块表示本公开方案，与常规方案相比，本公开方案可使曲轴最大挠度降低71％，曲轴最大接触应力降低25％，不仅大幅降低了压缩机的振动水平，还可减少曲轴与法兰间的磨损，提高零件可靠性。
1.本公开下滚子质量小于上滚子质量，下滚子可为空心结构、带支撑的空心结构或者使用轻质化材料；
2.针对空心的第二滚子9，第二滚子9径向内壁90A的厚度和径向外壁90B的厚度应满足以下关系：
Figure PCTCN2022140632-appb-000008
第二滚子9位于上方的第一轴向端部90C的厚度与位于下方的第二轴向端部90D的厚度应满足以下关系：
Figure PCTCN2022140632-appb-000009
3.针对带支撑部95的空心的第二滚子9，应满足如下关系：
Figure PCTCN2022140632-appb-000010
Figure PCTCN2022140632-appb-000011
4.电机转子3上方和下方仅有一个平衡块1，平衡块1可位于电机转子3上方，亦可位于电机转子3下方，平衡块1位于曲轴2下方的第二偏心部21一侧，且质心位于曲轴2的第一偏心部20和第二偏心部21质心轴线的平面内；
5.第一滚子6、第二滚子9及平衡块1各自的质量、偏心距和各距离间存在如下关系：
Figure PCTCN2022140632-appb-000012
6.平衡块1为扁平化结构，由铆钉固定在电机转子3上方或下方。
本公开解决了如下技术问题
1.压缩机在高频下振动和噪音水平加剧恶化，尤其对于高速压缩机更为严重；
2.相关技术中平衡系统平衡块体积和质量大，风阻大，电机驱动功耗较大；
3.相关技术中平衡系统双平衡块及实心滚子的压缩机重量重，成本高；
本公开具有以下有益效果：
1.减少平衡块数量，大幅降低曲轴挠度，减小压缩机振动和噪音水平；
2.减小曲轴与法兰直接的接触应力(由于重量小，离心力变小，对应到曲轴和法兰接触位置的接触应力减小)，提高压缩机可靠性；
3.由于滚子变轻，摩擦功耗小(跟法兰、中间隔板以及气缸)，还可以是由于曲轴与法兰的接触应力变小，因此减小电机驱动耗功，提高能效；
4.减少平衡块数量及重量，减轻下滚子重量，节省成本。
在一些实施方式中，第一滚子6位于电机转子3与第二滚子9之间，第二滚子9相对于第一滚子6远离电机转子3。这是本公开的优选结构形式，即如图5所示，电机转子3、第一滚子6和第二滚子9上下依次排布，第一滚子6和第二滚子9的质心分别位于曲轴2的轴线的两侧。
在一些实施方式中，平衡块1设置于电机转子3上，且沿曲轴2的轴线位于远离第一滚子6的轴向一端；或者，平衡块1设置于电机转子3上，且沿曲轴2的轴线位于靠近第一滚子6的轴向另一端。如图5所示的主实施例中，平衡块1沿曲轴2的轴线设置于电机转子3的远离第一滚子6的一端；如图10所示的替代实施例1中，平衡块1沿曲轴2的轴线设置于电机转子3的靠近第一滚子6的一端。
替代实施例1：如图10所示，根据上滚子(第一滚子6)与下滚子(第二滚子9)之间的质量差，亦可将平衡块1设置与电机转子3下方位置，将其作为主平衡块，去掉副平衡块，该方案可以使曲轴2顶端的挠度更小，但有可能会引起曲轴最大挠度发生在上偏心部(第一偏心部20)位置，此时需评估曲轴变形量对上气缸7中上滚子运行的影响，如果曲轴2在上偏心部(第一偏心部20)位置挠度过大可能会引起滚子与气缸卡死或泄露等问题，但如果该处曲轴变形仍在接受范围内，则该方案较单副平衡块方案具有更好的振动水平。
在一些实施方式中，空心部90为一个，空心部90为环形空腔，第二滚子被环形空腔分隔成径向内壁90A、径向外壁90B、第一轴向端部90C和第二轴向端部90D，径向内壁90A的径向厚度为b，径向外壁90B的径向厚度为a，第一轴向端部90C的轴向厚度为c，第二轴向端部90D的轴向厚度为d，第二滚子9的径向总厚度为t，第二滚子9的轴向总厚度为h，并满足下列关系：
Figure PCTCN2022140632-appb-000013
图7为本公开的第二滚子9为空心结构的示意图，第二滚子9位于下方，其内壁面91与曲轴2的第二偏心部21接触，上端面92与隔板8的下端面接触，内壁面91上下设置有第一倒角93和第二倒角94；空心部90的设计决定了径向外壁90B的径向厚度a、径向内壁90A的径向厚度b、第一轴向端部90C的轴向厚度c、第二轴向端部90D的轴向厚度d的尺寸，由于第二滚子9位于气缸内，当冷媒压缩时滚子内外圆都会承受较大的载荷，故径向外壁90B的径向厚度a、径向内壁90A的径向厚度b不宜过薄，不然会引起内外壁向中间凹陷，进而导致冷媒从高压腔向低压腔泄漏及滚子、滑片等零件的磨损等问题，经研究第二滚子9的内外壁厚应满足以下关系：
Figure PCTCN2022140632-appb-000014
第二滚子9的上下端面也具有较高的油膜压力，故第二轴向端部90D的轴向厚度c、第二轴向端部90D的轴向厚度d也不宜过薄，不然会引起上下壁向内凹陷，进而导致冷媒从第二滚子9的端面进行泄漏及第二滚子9与下法兰11和隔板8的零件磨损问题，经研究第二滚子9的的上下壁厚应满足以下关系：
Figure PCTCN2022140632-appb-000015
在一些实施方式中，空心部90为两个，且两个空心部90沿第二滚子9的轴向间隔设置，且在两个空心部90之间具有支撑部95，两个空心部90的径向内壁90A的径向厚度均为b1，两个空心部90的径向外壁90B的径向厚度均为a1，其中一个空心部90的远离另一个空心部90一侧的第三轴向端部90E的轴向厚度为c1，另一个空心部90的远离一个空心部90一侧的第四轴向端部90F的轴向厚度为d1，第二滚子9的径向总厚度为t，第二滚子9的轴向总厚度为h，并满足下列关系：
Figure PCTCN2022140632-appb-000016
Figure PCTCN2022140632-appb-000017
在一些实施方式中，支撑部95的轴向厚度为e1，并且有：
Figure PCTCN2022140632-appb-000018
替代实施例2：如图11所示，第二滚子9亦可做成空心部带支撑部95的结构，这样可以更大程度的减小第二滚子9内外壁的变形，预防滚子冷媒泄漏及零件磨损等问题。为保证支撑结构有较好的支撑效果，支撑部95的厚度应满足如下关系：
Figure PCTCN2022140632-appb-000019
由于带了支撑结构，第二滚子9的上下左右壁厚可满足如下关系：
Figure PCTCN2022140632-appb-000020
Figure PCTCN2022140632-appb-000021
原始空心滚子方案结构设置合理亦不会产生较大的变形，该替代实施例可以更大程度的减小变形，但会相应的增加加工成本，故更适用于对空心滚子变形量要求更高的压缩机。
在一些实施方式中，空心部个数为n，n个空心部90依次沿第二滚子9的轴向间隔设置，其中n≥1；第二滚子9的径向总厚度为t，第二滚子9的轴向总厚度为h；
n个空心部90的径向外壁90B的径向厚度均为a，n个空心部90的径向内壁90A的径向厚度均为a，并有a≥t/(2(n+1))，b≥t/(2(n+1))；
n个空心部90中，每个空心部90的轴向一端的轴向厚度为c，且每个空心部90的轴向另一端的轴向厚度为d，并有c≥h/(4(n+1))，d≥h/(4(n+1))；
n个空心部90中相邻两个空心部90之间具有支撑部95，多个支撑部95的轴向厚度均相等且为e，并有e≥h/(8(n+1))。
这是本公开的第三实施例的优选结构形式，该替代实施例可以更大程度的减小变形，但会相应的增加加工成本，故更适用于对空心滚子变形量要求更高的压缩机。
在一些实施方式中，压缩机为立式压缩机，第一滚子6和第二滚子9上下布置，且第一滚子6位于第二滚子9的上方，电机转子3位于第一滚子6的上方，平衡块1设置于电机转子3的上端面或设置于电机转子3的下端面。
在一些实施方式中，第一滚子6和第一偏心部20的质量为m1，第一质心距离曲轴的轴线的最小距离为r1，第二滚子9和第二偏心部21的质量为m0，第二质心距离曲轴的轴线的最小距离为r0，平衡块1的质量为m2，平衡块1的质心距离曲轴的轴线的最小距离为r2，并满足下列关系：
Figure PCTCN2022140632-appb-000022
图8为本公开平衡系统的结构尺寸示意图，上偏心量r1等于下偏心量r0，由于上下偏心质量存在差异，故需在电机转子3上部设置平衡块1，为了使整个平衡系统有较小的曲轴挠度，需满足受力平衡和力矩平衡方案，并根据研究经验，上下滚子及平衡块质量、偏心距和各距离间存在如下关系：
Figure PCTCN2022140632-appb-000023
在一些实施方式中，第一滚子6和第一偏心部20的质量为m1，第一质心距离曲轴的轴线的最小距离为r1，第二滚子9和第二偏心部21的质量为m0，第二质心距离曲轴的轴线的最小距离为r0，平衡块1的质量为m2，平衡块1的质心距离曲轴的轴线的最小距离为r2，沿曲轴2的轴线方向，第一质心与第二质心之间存在距离l1，平衡块1的质心与第二质心之间存在距离l2，存在如下关系：
Figure PCTCN2022140632-appb-000024
本公开还提供一种空调器，其包括前任一项的压缩机。
替代实施例3：下滚子不仅可以通过空心化来实现上下滚子之间的质量差，还可以使 用不同的滚子材料来实现该功能，例如上滚子仍使用传统FC300等铸铁材料，下滚子采用密度更轻的材料，例如陶瓷、铝合金、钛合金等轻质材料，通过上下滚子密度差来达到质量差的目的。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各方式的有利技术特征可以自由地组合、叠加。
以上仅为本公开的较佳实施例而已，并不用以限制本公开，凡在本公开的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本公开的保护范围之内。以上仅是本公开的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本公开技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本公开的保护范围。

Claims (11)

  1. 一种压缩机，包括：
    曲轴(2)，所述曲轴(2)包括第一偏心部(20)和第二偏心部(21)，所述第一偏心部(20)和所述第二偏心部(21)分别位于所述曲轴(2)的不同的轴段上；
    第一滚子(6)，套设于所述第一偏心部(20)的外周，所述第一滚子(6)的内部为实心结构；
    第二滚子(9)，套设于所述第二偏心部(21)的外周，所述第二滚子(9)的内部具有空心部(90)，形成空腔；
    电机转子(3)，套设于所述曲轴(2)；和
    平衡块(1)，仅设置于所述电机转子(3)沿轴向的一端；
    其中，所述第一偏心部(20)和所述第一滚子(6)的质心为第一质心，所述第一质心的轴线经过所述第一质心且与所述曲轴(2)的轴线平行，所述第二偏心部(21)和所述第二滚子(9)的质心为第二质心，所述第二质心的轴线经过所述第二质心且与所述曲轴(2)的轴线平行，且所述平衡块(1)的质心、所述第一质心的轴线和所述第二质心的轴线位于同一平面内；
    并且在所述平面内，所述第一质心位于所述曲轴(2)的轴线的第一侧，所述平衡块(1)的质心位于所述曲轴(2)的轴线的第二侧，使得所述曲轴(2)的轴线位于所述平衡块(1)的质心与所述第一质心之间，所述第二质心位于所述曲轴(2)的轴线的所述第二侧。
  2. 根据权利要求1所述的压缩机，其中所述第一滚子(6)沿所述轴向位于所述电机转子(3)与所述第二滚子(9)之间。
  3. 根据权利要求2所述的压缩机，其中所述平衡块(1)设置于所述电机转子(3)上，且沿所述曲轴(2)的轴线位于远离所述第一滚子(6)的一端；或者，所述平衡块(1)设置于所述电机转子(3)上，且沿所述曲轴(2)的轴线位于靠近所述第一滚子(6)的一端。
  4. 根据权利要求1～3任一项所述的压缩机，其中所述空心部(90)为一个，所述空心部(90)为环形空腔，所述第二滚子(9)被所述环形空腔分隔成径向内壁(90A)、径向外壁(90B)、第一轴向端部(90C)和第二轴向端部(90D)，所述径向内壁(90A)的径向厚度为b，所述径向外壁(90B)的径向厚度为a，第一轴向端部(90C)的轴向厚度 为c，第二轴向端部(90D)的轴向厚度为d，所述第二滚子(9)的径向总厚度为t，所述第二滚子(9)的轴向总厚度为h，并满足下列关系：
    Figure PCTCN2022140632-appb-100001
    Figure PCTCN2022140632-appb-100002
  5. 根据权利要求1～4任一项所述的压缩机，其中所述空心部(90)为两个，且两个所述空心部(90)沿所述第二滚子(9)的轴向间隔设置，且在两个所述空心部(90)之间具有支撑部(95)，两个所述空心部(90)的径向内壁(90A)的径向厚度均为b1，两个所述空心部(90)的径向外壁(90B)的径向厚度均为a1，其中一个空心部(90)的远离另一个空心部(90)一侧的第三轴向端部(90E)的轴向厚度为c1，另一个空心部(90)的远离一个空心部(90)一侧的第四轴向端部(90F)的轴向厚度为d1，所述第二滚子(9)的径向总厚度为t，所述第二滚子(9)的轴向总厚度为h，并满足下列关系：
    Figure PCTCN2022140632-appb-100003
  6. 根据权利要求5所述的压缩机，其中所述支撑部(95)的轴向厚度为e1，并且
    Figure PCTCN2022140632-appb-100004
  7. 根据权利要求1～6任一项所述的压缩机，其中所述空心部个数为n，n个所述空心部(90)依次沿所述第二滚子(9)的轴向间隔设置，其中n≥1；所述第二滚子(9)的径向总厚度为t，所述第二滚子(9)的轴向总厚度为h；
    n个所述空心部(90)的径向外壁(90B)的径向厚度均为a，n个所述空心部(90)的径向内壁(90A)的径向厚度均为a，并有a≥t/(2(n+1))，b≥t/(2(n+1))；
    n个所述空心部(90)中，每个所述空心部(90)的轴向一端的轴向厚度为c，且每个所述空心部(90)的轴向另一端的轴向厚度为d，并有c≥h/(4(n+1))，d≥h/(4(n+1))；
    n个所述空心部(90)中相邻两个空心部(90)之间具有支撑部(95)，多个支撑部(95)的轴向厚度均相等且为e，并有e≥h/(8(n+1))。
  8. 根据权利要求1～7任一项所述的压缩机，其中所述压缩机为立式压缩机，所述第一滚子(6)和所述第二滚子(9)上下布置，且所述第一滚子(6)位于所述第二滚子(9)的上方，所述电机转子(3)位于所述第一滚子(6)的上方，所述平衡块(1)设置于所述电机转子(3)的上端面或设置于所述电机转子(3)的下端面。
  9. 根据权利要求1～8任一项所述的压缩机，其中所述第一滚子(6)和所述第一偏心部(20)的质量为m1，所述第一质心距离所述曲轴(2)的轴线的最小距离为r1，所述第二滚子(9)和所述第二偏心部(21)的质量为m0，所述第二质心距离所述曲轴(2)的 轴线的最小距离为r0，所述平衡块(1)的质量为m2，所述平衡块(1)的质心距离所述曲轴(2)的轴线的最小距离为r2，并满足下列关系：
    Figure PCTCN2022140632-appb-100005
  10. 根据权利要求1～9任一项所述的压缩机，其中所述第一滚子(6)和所述第一偏心部(20)的质量为m1，所述第一质心距离所述曲轴(2)的轴线的最小距离为r1，所述第二滚子(9)和所述第二偏心部(21)的质量为m0，所述第二质心距离所述曲轴(2)的轴线的最小距离为r0，所述平衡块(1)的质量为m2，所述平衡块(1)的质心距离所述曲轴的轴线的最小距离为r2，沿所述曲轴(2)的轴线方向，所述第一质心与所述第二质心之间存在距离l1，所述平衡块(1)的质心与所述第二质心之间存在距离l2，存在如下关系：
    Figure PCTCN2022140632-appb-100006
  11. 一种空调器，包括权利要求1～10任一项所述的压缩机。
PCT/CN2022/140632 2022-05-30 2022-12-21 压缩机和空调器 WO2023231383A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202210603409.7A CN114857005A (zh) 2022-05-30 2022-05-30 一种压缩机和空调器
CN202210603409.7 2022-05-30

Publications (1)

Publication Number Publication Date
WO2023231383A1 true WO2023231383A1 (zh) 2023-12-07

Family

ID=82641176

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/140632 WO2023231383A1 (zh) 2022-05-30 2022-12-21 压缩机和空调器

Country Status (2)

Country Link
CN (1) CN114857005A (zh)
WO (1) WO2023231383A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114857005A (zh) * 2022-05-30 2022-08-05 珠海格力电器股份有限公司 一种压缩机和空调器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20110120105A (ko) * 2010-04-28 2011-11-03 엘지전자 주식회사 밀폐형 압축기
CN109139477A (zh) * 2018-11-07 2019-01-04 珠海格力节能环保制冷技术研究中心有限公司 一种曲轴转子组件和压缩机
CN208831239U (zh) * 2018-08-31 2019-05-07 广东美芝精密制造有限公司 旋转压缩机
CN110873051A (zh) * 2018-08-31 2020-03-10 广东美芝精密制造有限公司 双缸旋转式压缩机及其曲轴
CN210422936U (zh) * 2019-08-27 2020-04-28 珠海凌达压缩机有限公司 曲轴组件、压缩机和空调器
JP2020186660A (ja) * 2019-05-10 2020-11-19 三菱重工サーマルシステムズ株式会社 ロータリ圧縮機
CN114215753A (zh) * 2021-12-20 2022-03-22 珠海格力电器股份有限公司 一种曲轴、泵体结构、压缩机及空调器
CN114857005A (zh) * 2022-05-30 2022-08-05 珠海格力电器股份有限公司 一种压缩机和空调器
CN217481535U (zh) * 2022-05-30 2022-09-23 珠海格力电器股份有限公司 一种压缩机和空调器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20110120105A (ko) * 2010-04-28 2011-11-03 엘지전자 주식회사 밀폐형 압축기
CN208831239U (zh) * 2018-08-31 2019-05-07 广东美芝精密制造有限公司 旋转压缩机
CN110873051A (zh) * 2018-08-31 2020-03-10 广东美芝精密制造有限公司 双缸旋转式压缩机及其曲轴
CN109139477A (zh) * 2018-11-07 2019-01-04 珠海格力节能环保制冷技术研究中心有限公司 一种曲轴转子组件和压缩机
JP2020186660A (ja) * 2019-05-10 2020-11-19 三菱重工サーマルシステムズ株式会社 ロータリ圧縮機
CN210422936U (zh) * 2019-08-27 2020-04-28 珠海凌达压缩机有限公司 曲轴组件、压缩机和空调器
CN114215753A (zh) * 2021-12-20 2022-03-22 珠海格力电器股份有限公司 一种曲轴、泵体结构、压缩机及空调器
CN114857005A (zh) * 2022-05-30 2022-08-05 珠海格力电器股份有限公司 一种压缩机和空调器
CN217481535U (zh) * 2022-05-30 2022-09-23 珠海格力电器股份有限公司 一种压缩机和空调器

Also Published As

Publication number Publication date
CN114857005A (zh) 2022-08-05

Similar Documents

Publication Publication Date Title
CN1108453C (zh) 涡旋式气体压缩机
WO2018094891A1 (zh) 用于涡旋压缩机的涡旋盘、涡旋压缩机和制冷设备
WO2023231383A1 (zh) 压缩机和空调器
Teh et al. Theoretical study of a novel refrigeration compressor–Part I: Design of the revolving vane (RV) compressor and its frictional losses
CN111287975B (zh) 泵体组件及压缩机
CN112343820B (zh) 一种多层滚子式压缩机及使用其的空调
US20220090596A1 (en) Compressor and refrigeration device
KR100432115B1 (ko) 복수 실린더 로터리 압축기
CN217481535U (zh) 一种压缩机和空调器
WO2016086396A1 (zh) 低背压旋转式压缩机
WO2022116577A1 (zh) 泵体组件及具有其的流体机械
CN208845360U (zh) 双缸旋转式压缩机及用于双缸旋转式压缩机的曲轴
JP4065654B2 (ja) 複数シリンダロータリ圧縮機
CN205089618U (zh) 多缸旋转式压缩机
CN211819906U (zh) 转子压缩机的泵体组件、转子压缩机和空调器
CN114320915A (zh) 泵体组件、压缩机及制冷制热设备
CN210949139U (zh) 压缩机和制冷设备
CN113757122A (zh) 一种隔板组件、泵体组件及压缩机
JP6739660B1 (ja) スクロール圧縮機
CN111059136A (zh) 曲轴及滚子配合结构、压缩机、空调器
CN216044418U (zh) 一种隔板组件、泵体组件及压缩机
JP6502078B2 (ja) 圧縮機
CN218177407U (zh) 滑片、泵体组件和压缩机
KR102372174B1 (ko) 로터리 압축기
JP6071787B2 (ja) ロータリ圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22944684

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2022944684

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2022944684

Country of ref document: EP

Effective date: 20240821