A rotor compressor

Abstract

The present invention discloses a rotor compressor, comprising a compressor barrel and a cylinder, wherein the inner diameter of the compressor barrel and the inner diameter of the cylinder satisfy the following relationship: wherein: D is the cylinder diameter, D1 is the inner diameter of the compressor barrel, L1 is the distance between the slider and the end face of the missed hole when the slider is retracted, and δ1 is the distance between the outer end face of the missed hole and the inner wall of the cylinder. The relationship between the barrel and the inner diameter of the cylinder in the compressor reduces the spring length to a certain extent, effectively avoiding the problem of the spring and slider not being able to work normally and the compressor failing due to the poor spring stability caused by the excessive length of the spring.

Description

Technical Field

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

[0002] With the development of technology, the energy efficiency requirements of rotary compressors are getting higher and higher. In order to improve energy efficiency, a reasonable relationship between the inner diameter of the barrel and the compressor cylinder is required to optimize the compressor cost and energy efficiency.

[0003] When the cylinder inner diameter remains unchanged, the larger the compressor cylinder inner diameter, the larger the compressor displacement can be arranged at the same cylinder height. When the same cooling capacity is required, the smaller the compressor cylinder diameter, the lower the compressor cost under the same material. However, if the relationship between the cylinder and cylinder inner diameter is not appropriate, the compressor spring and slider will not work properly, resulting in compressor failure. Summary of the invention

[0004] The object of the present invention is to provide a rotor type compressor which can effectively solve the problem of compressor failure.

[0005] To this end, the rotary compressor provided by the present invention includes a compressor barrel and a cylinder, and the inner diameter of the compressor barrel and the inner diameter of the cylinder satisfy the following relationship:

[0006]

[0007] Where: D is the cylinder diameter, D1 is the inner diameter of the compressor barrel, L1 is the distance between the slider and the end face of the leaky hole when it is retracted, and δ1 is the distance between the outer end face of the leaky hole and the inner wall of the cylinder.

[0008] In some embodiments, the δ is 3.5-7 mm.

[0009] In some embodiments, the L1 is 0.6-3 mm.

[0010] The technical problems that can be solved by adopting this technical solution include at least:

[0011] 1) The relationship between the barrel and the inner diameter of the cylinder in the compressor solves to a certain extent the problem of unreasonable cylinder arrangement, which leads to excessive length of the spring and poor stability, resulting in the failure of the spring and slider to work normally and the failure of the compressor.

[0012] 2) This compression solves to a certain extent the problem that the spring slider cannot be installed due to the cylinder diameter being too large.

[0013] 3) The distance between the outer end surface of the compressor leakage hole and the inner wall of the cylinder is configured to be 3.5-7mm, which to a certain extent solves the problem of spring installation failure caused by the thin edge of the cylinder. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] The drawings herein are incorporated into and constitute a part of the specification, showing embodiments consistent with the present invention, and together with the specification, are used to explain the principles of the present invention. Obviously, the drawings described below are only some embodiments of the present invention, and for those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative work. In the drawings:

[0015] Figure 1 It is a schematic diagram of the structure of the rotor compressor recorded in the present invention;

[0016] Figure 2 It is a structural schematic diagram of the rotary compressor cylinder recorded in the present invention;

[0017] Figure 3 It is a schematic cross-sectional view of the barrel and cylinder of the rotary compressor recorded in the present invention;

[0018] Figure 4 A diagram showing the relationship between the cross-sectional dimensions of the barrel and cylinder of the rotary compressor recorded in the present invention;

[0019] Figure 5 It is a structural schematic diagram of the compressor system recorded in the present invention;

[0020] Figure 6 A schematic diagram of the structure of the air intake hole recorded in the present invention;

[0021] Figure 7 for Figure 6 Floor plan of

[0022] Figure 8 Another structural schematic diagram of the air intake hole recorded in the present invention;

[0023] Fig. 9 for Figure 8 Floor plan of

[0024] Fig.10 It is a schematic diagram of the steel-copper structure of the cylinder cannula recorded in the present invention;

[0025] Fig.11 It is a structural schematic diagram of the conical guide section of the cylinder insert pipe recorded in the present invention;

[0026] Fig.12 It is a structural schematic diagram of the cylinder pipe shrinkage guide section recorded in the present invention;

[0027] Fig.13 It is an assembly diagram of the rotor outer circle and the cylinder recorded in the present invention. DETAILED DESCRIPTION

[0028] Example embodiments will now be described more fully with reference to the accompanying drawings. However, example embodiments can be implemented in many forms and should not be construed as limited to the examples set forth herein; rather, these embodiments are provided so that the invention will be more comprehensive and complete and fully convey the concept of the example embodiments to those skilled in the art.

[0029] The present invention provides a rotor type compressor, the inner diameter of the barrel of the compressor and the inner diameter of the cylinder satisfy a certain relationship, so that the barrel and the cylinder are selected more reasonably, the compressor has higher energy efficiency and better safety.

[0030] like Figure 1 As shown, the rotary compressor of the present disclosure includes a cylinder 101, an air inlet 102, a spring 103, a slider 104, an exhaust valve 105, a rotor 107 installed in the cavity of the cylinder 101, a crankshaft 106 assembled with the rotor 107, and a compressor barrel 109. Gas enters from the air inlet 102 and is discharged through the exhaust valve 105 after being compressed.

[0031] Combination Figure 2-4 The cylinder 101 includes a first assembly end 1011, a second assembly end 1012 and an assembly body 1013 with an assembly cavity assembled between the first assembly end 1011 and the second assembly end 1012. The first assembly end 1011 is provided with a missed hole 110 for assembling one end of the slider 104. The missed hole 110 is a non-closed hole, including a first open end and a second open end. With the first open end and the second open end as starting points, the opening extends toward the assembly body 1013 to form a slideway 111 for providing sliding for the slider 104; one end of the slider 104 assembled in the missed hole 110 is assembled together with one end of the spring 103, and the other end of the spring 103 is assembled on the inner side wall of the first assembly end 1011. The rotor 107 is configured to be located in the assembly cavity of the assembly 1013, and can slide along the inner wall of the cavity of the assembly under the action of the electric field force to achieve gas compression. When the spring 103 is in an extended state, the end of the slider 104 contacts the outer wall of the rotor 107. Under the action of the spring 103 and the rotor 107, the slider 104 slides in the slideway 111 to achieve gas compression.

[0032] In the present disclosure, the crankshaft 106 has an eccentric part and an eccentricity e. The crankshaft 106 transmits the rotational force of the motor to the rotor 107. The eccentric part of the crankshaft drives the piston to rotate in the assembly cavity of the assembly body, and the volume formed by the rotor and the cylinder is changed by the eccentricity e, thereby realizing gas compression; and the slider reciprocates in the cylinder slide groove through the eccentric part and the eccentricity e. The slider 104 is compressed by the elastic force of the spring 103, so that the slider 104 and the rotor 107 are closely combined to isolate the high-pressure chamber and the low-pressure chamber.

[0033] In the present disclosure, the inner diameter of the compressor barrel 109 and the inner diameter of the cylinder 101 satisfy the following relationship: D = Where: D is the cylinder diameter, D1 is the inner diameter of the compressor cylinder, L1 is the distance between the slider and the end face of the leak hole when it is retracted, and δ1 is the distance between the outer end face of the leak hole and the inner wall of the cylinder. Figure 4 shown.

[0034] In the present disclosure, the crankshaft eccentricity e of the crankshaft 6 is (0.05-0.1D), and the slider length L=4-7e=(0.20-0.7)D.

[0035] The compressor disclosed in the present invention makes the selection of the compressor cylinder body and the barrel diameter more reasonable through the relationship between the barrel diameter and the inner diameter of the cylinder body, the compressor has higher energy efficiency and better reliability.

[0036] In order to illustrate the specific design method provided by the present invention, the rotor compressor cylinder diameters of Φ88, Φ100, Φ107, and Φ110 using R32 working fluid are used as examples for explanation:

[0037]

[0038] D represents the calculated cylinder diameter, D' is the actual cylinder diameter after rounding; D1 is the inner diameter of the cylinder, and D1-1 is the inner diameter of the cylinder D1 minus 1mm; the units max and min in the table represent the maximum and minimum inner diameters of the cylinder at this cylinder diameter.

[0039] The inner diameter relationship between the compressor barrel and the cylinder provided by the present invention is applicable to rotary compressors in any refrigerant use occasion; applicable to rotary compressors in different application fields, such as air conditioning refrigeration, heat pump heating, freezing and refrigeration, etc.; applicable to rotary compressors with different displacements.

[0040] In the present disclosure, a first assembly end 1011 of the cylinder 101 is provided with an air suction hole 3 for communicating with the assembly cavity, and for communicating with an external auxiliary device.

[0041] like Figure 5 As shown, a compressor body 1 and a gas-liquid separator 2 are configured. The gas-liquid separator 2 (also called a liquid reservoir) is connected to the air intake hole 3 and is used to separate the liquid refrigerant that is not completely vaporized to ensure that the refrigerant entering the compressor cylinder 101 is dry steam.

[0042] The connection between the air inlet pipe 201 of the gas-liquid separator 2 and the pipeline is a copper tube welding type. The refrigerant enters the gas-liquid separator 2 through the pipeline. The outlet elbow 202 of the gas-liquid separator 2 is connected to the air intake hole 3 through the connecting pipe 5 and the cylinder insert pipe 4, so as to realize the connection between the gas-liquid separator 2 and the cylinder 101. Specifically, the connecting pipe 5 is a copper-steel structural part. The copper pipe and the steel pipe are connected by brazing in the furnace to form a copper-steel structural part, including a steel pipe end 501 and a copper sleeve end 502. The connecting pipe 5 extends out of the compressor body 1. The steel pipe end 501 has a bell mouth and is connected to the cylinder 109 of the compressor body 1 by resistance projection welding. One end of the cylinder insert pipe 4 is inserted into the copper sleeve end 502 and extends into the air intake hole 3. The copper sleeve end 502 is brazed with the cylinder insert pipe 4 and the air outlet elbow 202.

[0043] In the present disclosure, the cylinder insert 4 can be configured as a copper steel structure, such as Fig.10 As shown. The copper tube and the steel tube are connected by furnace brazing to form a copper-steel structure, including a steel tube part and a copper tube part. The steel tube part is inserted into the air intake hole 3 and sealed by interference fit, and the copper tube part is brazed to the connecting tube and the air outlet elbow.

[0044] Since the compressor body 1 and the gas-liquid separator 2 are processed and manufactured separately, and the two are connected through the cylinder insert 4 and the connecting pipe 5, the outer circle of the steel pipe part of the cylinder insert 4, the size and shape tolerance of the air intake hole need to be high precision. Otherwise, when the cylinder insert 4 is configured as a copper-steel structural part, the steel pipe part needs to be installed into the air intake hole 3 with a large insertion force, which is easy to destroy the assembly precision of the compressor body that has been fixed in the core. Fig.13 As shown in the figure, when the size is larger, the CP gap increases or the centering angle deviates from the design value, the refrigerant leakage increases during the operation of the compressor, and the volumetric efficiency decreases. The CP gap in this disclosure refers to the gap between the outer diameter of the rotor and the inner diameter of the cylinder. Fig.13 The 0.02 in the figure is the CP gap.

[0045] To this end, the present invention configures the cylinder tube 4 as a full copper structural part, and the intake hole material is cast iron or powder metallurgy material. The copper cylinder tube 4 is interference connected with the intake hole 3. Due to the plasticity of the copper material, the two can be connected with a larger interference fit under a smaller installation force, ensuring a reliable seal between the cylinder tube 4 and the intake hole 3.

[0046] In the present disclosure, the cylinder insert tube 4 includes an A end and a B end, wherein the A end is used to be inserted into the air intake hole 3 and connected with the air intake hole 3 by interference fit, and the B end of the cylinder insert tube 4 is used to communicate with the auxiliary equipment. Fig.11 , 12 As shown, the A end of the cylinder insert 4 includes a fitting section 401 and a guide section 402. The fitting section 401 is interference fit with the air intake hole 3, and the guide section 402 plays a guiding role when the cylinder insert 4 is inserted into the air intake hole 3 and is easy to insert.

[0047] like Fig.11 As shown, the front end of the guide section 402 is a conical structure with a length of ι, a value range of 1mm≤ι≤5mm, a minimum outer diameter of the guide section 402 of Φdc, and when the outer diameter of the matching section 402 is ΦD, Φdc / ΦD≥98%.

[0048] like Fig.12 As shown, the guide section 402 is a cylindrical surface. When it is a cylindrical surface, the end size is smaller than the size of other parts of the guide section 402, which is convenient for inserting the cylinder insert 4, and the matching section 401 and the guide cylindrical surface are smoothly transitioned. Under this structure, the length of the guide section 402 is ι, and the value range is 1mm≤ι≤5mm. Its outer diameter Φdc is slightly smaller than the outer diameter ΦD of the matching section, and the ratio of the two is ≥98%.

[0049] The ratio disclosed in the present invention realizes effective guidance. If the ratio is too large, there is no guiding effect. If the ratio is too small, the effective flow area of ​​the inner diameter of the cylinder tube 4 is reduced by the square of the radius, which increases the flow resistance of the refrigerant.

[0050] It should be understood that the above description of the cylinder insert 4 made of all copper is also applicable to the cylinder insert of steel-copper structure.

[0051] The advantage of copper cylinder insert is its strong plasticity, but its disadvantage is its soft material. When the cylinder insert is pressed into the cylinder suction hole, the outer circle of the insert acts on the edge of the suction hole, generating copper chips. During the suction process of the compressor, the copper chips are brought into the pump body by the refrigerant gas, which can easily cause the movement to jam. Figure 6 , 7 As shown, the suction hole 3 of the present invention has a flared section 301 at the end of the cylinder cannula, and the straight section 302 is connected to the flared section 301. The flared generatrix of the flared section 301 is an arc, the arc radius is r, 1mm≤r≤10mm, r is tangent to the straight section 302, and the arc depth is 1mm≤h≤3mm. The arc intersects with the outer circle of the cylinder to form an intersection line 5 which is a circle with a diameter of D. The diameter of the straight section 302 of the suction hole 3 is d, d / D>0.90, and the ratio is adjusted to 0.9 here. If the ratio is too large, the flaring cannot play a guiding role, and if the ratio is too small, the distance between the intersection line and the cylinder end face becomes smaller.

[0052] This structure enables the outer circle of the cylinder insert tube 4 to contact the expanded arc of the air intake hole 3 when the cylinder insert tube 4 is pressed into the cylinder air intake hole 3, and an interference fit is achieved through extrusion deformation.

[0053] The flared section 301 forms a smooth structure. The smooth flared structure tangent to the air intake hole 3 is to avoid copper chips from being generated during the process of the copper cylinder insert being pressed into the cylinder air intake hole.

[0054] like Figure 8 , 9As shown, in the present disclosure, the flared section 301 of the air intake hole 3 has a chamfer outward to form a chamfer structure, the chamfer depth is 1mm≤h≤3mm, the angle between the two sides of the chamfer is α, 5°≤α≤45°, and α and the straight section 302 of the air intake hole 3 are transitioned by a rounded corner R. The flared section 301 and the straight section 302 are transitioned by a rounded corner R, and the flared section 301 is a chamfered structure, forming a smooth transition to avoid the outer circle of the copper cylinder insert tube and the sharp edge of the air intake hole during the process of pressing the copper cylinder insert tube into the cylinder air intake hole, resulting in copper chips. When the copper chips are brought into the pump body by the refrigerant gas, it is easy to cause the movement to get stuck.

[0055] In the present disclosure, the cylinder insert 4 is configured as a thin-walled part, and the thickness δ is selected in the range of 0.4≤δ≤0.7, and the interference between the cylinder insert 4 and the cylinder air intake hole 3 is 0.02-0.09. If the thickness is selected too thin, the insert and the cylinder air intake hole are not sealed tightly, resulting in gas leakage. If the thickness is selected too thick, on the one hand, it wastes materials, and on the other hand, because the cylinder insert and the cylinder air intake hole are interference fit, the force required to install the cylinder insert increases, which is easy to damage the pump body structure that has been cored. Here, a set of copper tube thickness δ and interference fit range relationships are provided, see the following table:

[0056] Table 1 Relationship between δ and interference range

[0057] Delta value Optimal value of interference 0.4≤δ≤0.5 0.07～0.09 0.5≤δ≤0.6 0.04～0.07 0.6≤δ≤0.7 0.02～0.04

[0058] In the present invention, the outlet elbow 202 of the gas-liquid separator 2 is connected to the air intake port 3 through the cylinder insert pipe 4, and the air intake straight pipe of the liquid storage device is connected to the air conditioner pipeline, so that the low-temperature and low-pressure refrigerant gas is sucked into the cylinder cavity, and is compressed by the movement rotor to become a high-temperature and high-pressure gas, which is discharged from the compressor exhaust pipe 112.

[0059] The present invention adopts a copper cylinder cannula, which has a simple process, high efficiency and single parts. However, because the copper material is relatively soft, when it is connected with the cast iron part through interference, the edges of the cylinder suction hole are easily damaged and copper chips are generated on the surface. When the copper chips are brought into the pump body by the refrigerant gas, they are easily retained in the matching gap of the pump body structural parts, causing the pump body to be stuck and the compression to fail. The cylinder suction hole structure in this scheme adopts R angle or arc transition to avoid edges. At the same time, the reasonable cylinder cannula wall thickness and interference limit are limited, so that when the cylinder cannula is inserted into the cylinder suction hole, the outer circle of the cannula contacts with the expanded arc of the suction hole, and the interference fit is achieved through extrusion deformation.

[0060] In this solution, when the cylinder insert is configured as a copper-steel structural part, the two are connected by furnace brazing. The production cycle of parts is slow, and the outer circle of the steel pipe part needs to be finely ground to ensure the accuracy of the parts. Otherwise, when the steel pipe is pressed into the suction hole of the cast iron or powder metallurgy cylinder, it will hit each other hard, and the required installation force is large, which can easily destroy the assembly accuracy of the pump body that has been cored, resulting in an increase in the CP gap or a deviation of the centering angle from the design value, an increase in refrigerant leakage during the operation of the compressor, and a decrease in volumetric efficiency. However, the cylinder insert made of all copper material in this disclosure solves the problems existing in copper-steel structural parts and is more conducive to assembly.

[0061] Those skilled in the art should understand that the present invention includes but is not limited to the smooth outward flaring and chamfering transition of the cylinder air intake hole, and also includes other smooth structures for preventing the sharp edge of the air intake hole of the cast iron cylinder from scraping the outer circle of the copper cylinder insert during the interference fit insertion process, thereby generating copper chips.

[0062] The compressor body of the present invention can also adopt a rotary compressor as described in a fully enclosed rotary compressor (publication (notice) number: CN106678044A, publication (notice) date: 2017.05.17); or, a rotary compressor (publication (notice) number: CN104564681A, publication (notice) date: 2015.04.29); or, a horizontal micro compressor (publication (notice) number: CN103206381A, publication (notice) date: 2013.07.17); the suction hole 3 is opened at a position connected to the cylinder of the compressor, so that an auxiliary device such as a gas-liquid separator is connected to the cylinder, so that the refrigerant entering the cylinder is dry steam; or, the auxiliary device can be a refrigerant liquid storage tank, and the compressor is connected to the exhaust device through the cylinder inlet 4, so that the refrigerant directly enters the compressor cylinder.

[0063] The present disclosure has been described by the above-mentioned relevant embodiments, but the above-mentioned embodiments are only examples for implementing the present disclosure. It must be pointed out that the disclosed embodiments do not limit the scope of the present disclosure. On the contrary, changes and modifications made without departing from the spirit and scope of the present disclosure are all within the scope of patent protection of the present disclosure.

Claims

1. A rotary compressor, characterized in that: The invention comprises a cylinder, a spring, a slider, a rotor installed in the cylinder cavity, a crankshaft assembled with the rotor, and a compressor barrel, wherein the cylinder comprises a first assembly end, a second assembly end, and an assembly body with an assembly cavity assembled between the first assembly end and the second assembly end, and the first assembly end is provided with a knife hole for assembling one end of the slider; The knife leakage hole is a non-closed hole, including a first open end and a second open end, with the first open end and the second open end as starting points, extending the opening toward the assembly body to form a slideway for providing the sliding block; one end of the sliding block assembled in the knife leakage hole is assembled together with one end of the spring, and the other end of the spring is assembled on the inner side wall of the first assembly end; The rotor and the slider are used to compress the gas, and the inner diameter of the compressor barrel and the inner diameter of the cylinder satisfy the following relationship: Where: D is the cylinder diameter, D1 is the inner diameter of the compressor cylinder, L1 is the distance between the slider and the end face of the leakage hole when it is retracted, and δ1 is the distance between the outer end face of the leakage hole and the inner wall of the cylinder; The crankshaft eccentricity e of the crankshaft satisfies the following relationship: e=(0.05~0.1)D The length of the slider satisfies the following relationship: L=(0.2~0.7)D.

2. The compressor according to claim 1, characterized in that The δ1 is 3.5-7 mm.

3. The compressor according to claim 1, characterized in that The L1 is 0.6-3 mm.

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