Compressor and refrigeration apparatus

Abstract

This invention discloses a compressor and refrigeration equipment, relating to the field of compressor technology. The compressor includes a cylinder, a crankshaft, rollers, and vanes. The cylinder has a working chamber and a vane groove. Rollers are fitted onto the eccentric portion of the crankshaft, allowing eccentric rotation within the working chamber. Vanes reciprocate within the vane groove. The outer surface of the rollers has a connecting groove with an arc-shaped main body. The end of the vanes has a connecting portion including at least two arc surfaces, hinged within the connecting groove. The working chamber diameter, the eccentricity of the eccentric portion, the diameter of the arc-shaped main body, and the width of the connecting groove meet a defined range of comprehensive geometric characteristic parameters. This compressor, through its hinged structure and optimized dimensional parameters, effectively improves refrigerant leakage and frictional power consumption between the vanes and rollers, thereby enhancing the overall performance of the compressor.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] Rotary compressors are widely used in household air conditioners, heat pumps, and refrigeration equipment due to their compact structure, high efficiency, and good reliability. Currently, a new structure for rotary compressors connects rollers and vanes. This connection is achieved by placing the vane head into a hole in the roller that accommodates the vane head. However, this connection method still suffers from uneven contact stress distribution, which may lead to accelerated wear or jamming after long-term operation, affecting the long-term reliability of the compressor. Summary of the Invention

[0003] The main objective of this invention is to provide a compressor and refrigeration equipment, which aims to solve at least one of the technical problems mentioned in the background art.

[0004] To achieve the above objectives, the present invention proposes a compressor comprising a cylinder, a crankshaft, rollers, and vanes; the cylinder has a working chamber and a vane groove connected to the working chamber; the crankshaft is disposed within the working chamber and has an eccentric portion; the rollers are fitted onto the eccentric portion and are rotatably disposed within the working chamber; the vanes are reciprocally disposed within the vane groove, and the outer surface of the rollers has a connecting groove comprising an arc-shaped main body; the end of the vane has a connecting portion comprising at least two arc surfaces and is hinged within the connecting groove; Wherein, the diameter of the working cavity is D1, the eccentricity of the eccentric part is e, the diameter of the arc-shaped main body is D2, and the groove width of the connecting groove is L, satisfying: .

[0005] In one embodiment, the connecting portion includes a first arc segment, a second arc segment, and a third arc segment connected to each other, wherein the radius of curvature of the second arc segment is different from the radius of curvature of the first arc segment or the third arc segment.

[0006] In one embodiment, the radius of curvature of the second arc segment is greater than the radius of curvature of the first arc segment and the third arc segment.

[0007] In one embodiment, the diameter D2 of the arc-shaped main body is smaller than the thickness T of the slider.

[0008] In one embodiment, the width of the connecting groove satisfies 2.0mm≤L≤5.5mm.

[0009] In one embodiment, the roller is made of an alloy material with a Vickers hardness ≥400HV.

[0010] In one embodiment, the compressor uses difluoromethane as the refrigerant and the corresponding refrigeration oil is a synthetic ester oil or an ether oil.

[0011] In one embodiment, the refrigerant used in the compressor is a mixture of difluoromethane and pentafluoroethane, and the corresponding refrigeration oil is a synthetic ester oil or an ether oil.

[0012] In one embodiment, the compressor uses propane as the refrigerant and the corresponding refrigeration oil is a synthetic ester oil or a polyalkylene glycol oil.

[0013] The present invention also proposes a refrigeration device, which includes the compressor. The compressor includes a cylinder, a crankshaft, rollers, and vanes; the cylinder has a working chamber and a vane groove, which communicates with the working chamber; the crankshaft is disposed in the working chamber and has an eccentric portion; the rollers are fitted onto the eccentric portion and are rotatably disposed in the working chamber; the vanes are reciprocally disposed in the vane groove, and the outer surface of the rollers has a connecting groove, which includes an arc-shaped main body; the end of the vane has a connecting portion, which includes at least two arc surfaces and is hinged to the connecting groove. Wherein, the diameter of the working cavity is D1, the eccentricity of the eccentric part is e, the diameter of the arc-shaped main body is D2, and the groove width of the connecting groove is L, satisfying: .

[0014] The technical solution of this invention, by hingedly engaging the connecting portion of the vane end, which includes at least two arc surfaces, with the connecting groove of the roller outer surface with an arc-shaped main body, and by constraining the λ parameter, which is jointly defined by the working cavity diameter, the eccentricity of the eccentric portion, the diameter of the arc-shaped main body, and the width of the connecting groove opening, within a range of 0.4 to 3.0, effectively improves the problem of uneven contact stress distribution at the hinge of the vane and the roller, avoids accelerated wear or jamming during long-term operation, improves the sealing effect, reduces refrigerant leakage, reduces frictional power consumption, and significantly improves the reliability and operational stability of the compressor during long-term operation. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0016] Figure 1 This is a schematic diagram of the structure of an embodiment of the compressor provided by the present invention; Figure 2 for Figure 1 Schematic diagram of the middle cylinder; Figure 3 for Figure 1 Schematic diagram of the middle roller; Figure 4 for Figure 1 A schematic diagram of the hinged connection between the middle roller and the sliding plate; Figure 5 for Figure 4 A magnified view of a section at point A in the middle; Figure 6 for Figure 1 Schematic diagram of the middle slider; Figure 7 for Figure 1 Schematic diagram of the middle crankshaft; Figure 8 for Figure 4 A partial enlarged view of the connecting groove structure of the middle roller; Figure 9 This diagram illustrates the relationship between different compressor models λ and compressor efficiency (COP).

[0017] Explanation of icon numbers: 10. Cylinder; 11. Working chamber; 12. Sliding vane groove; 20. Crankshaft; 21. Eccentric part; 30. Roller; 31. Connecting groove; 40. Sliding vane; 41. Connecting part; 411. First arc segment; 412. Second arc segment; 413. Third arc segment.

[0018] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0020] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0021] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0022] Rotary compressors are widely used in household air conditioners, heat pumps, and refrigeration equipment due to their compact structure, high efficiency, and good reliability. Current rotary compressors employ a structure where rollers and vanes are connected together. This connection is achieved by placing the vane head into a hole in the roller that accommodates the vane head. However, this connection method still suffers from uneven contact stress distribution, potentially leading to accelerated wear or jamming after long-term operation, thus affecting the long-term reliability of the compressor. This invention proposes a compressor that solves at least one of the aforementioned technical problems.

[0023] Please see Figure 1 , Figure 2 , Figures 6 to 8 In one embodiment of the present invention, the compressor includes a cylinder 10, a crankshaft 20, rollers 30, and vanes 40; the cylinder 10 is provided with a working chamber 11, and the cylinder 10 is also provided with a vane groove 12, which is connected to the working chamber 11; the crankshaft 20 is disposed in the working chamber 11, and the crankshaft 20 has an eccentric portion 21; the eccentric portion 21 is fitted with rollers 30, and the rollers 30 are eccentrically rotatably disposed in the working chamber 11; the vanes 40 are reciprocally disposed in the vane groove 12, and the outer surface of the rollers 30 is provided with a connecting groove 31, which includes an arc-shaped main body portion; the end of the vane 40 is provided with a connecting portion 41, which includes at least two arc surfaces, and the connecting portion 41 is hinged in the connecting groove 31; Wherein, the diameter of the working cavity 11 is D1, the eccentricity of the eccentric part 21 is e, the diameter of the arc-shaped main body is D2, and the groove width of the connecting groove 31 is L, satisfying: .

[0024] Specifically, the compressor includes a cylinder 10, a crankshaft 20, rollers 30, and vanes 40. The cylinder 10 has a working chamber 11 for refrigerant compression. A vane groove 12 is also machined onto the cylinder 10, arranged radially along the cylinder 10 and communicating with the working chamber 11, providing installation space for the reciprocating motion of the vanes 40. The crankshaft 20 is assembled inside the working chamber 11, and an eccentric portion 21 is formed on the crankshaft 20, with an eccentricity of e. The rollers 30 are sleeved on the outside of the eccentric portion 21 of the crankshaft 20 and can rotate eccentrically within the working chamber 11 under the drive of the eccentric portion 21.

[0025] The slide plate 40 can reciprocate linearly along the extension direction of the slide plate groove 12 and is assembled inside the slide plate groove 12. A connecting groove 31 is formed on the outer surface of the outer peripheral wall of the roller 30. The connecting groove 31 is axially connected to the roller 30 and includes an arc-shaped main body with a diameter of D2. The groove opening width of the connecting groove 31 is L (which can be understood as the minimum width of the groove opening, or as the line connecting the start and end points of the arc-shaped main body). A connecting part 41 is formed at the end of the slide plate 40 facing the roller 30. The connecting part 41 is composed of at least two arc surfaces and is adapted to fit and hinge in the connecting groove 31 of the roller 30 to realize the hinged linkage between the slide plate 40 and the roller 30.

[0026] In this embodiment, the geometric dimensions such as the diameter D1 of the working cavity 11, the eccentricity e of the eccentric part 21, the diameter D2 of the arc-shaped main body, and the width L of the connecting groove 31 satisfy the formula: .

[0027] The geometric dimensions are in mm, and the arcsine function returns values ​​in radians. For example, when D1 is 43 mm, e is 4 mm, D2 is 3.2 mm, and L is 2.8 mm, the calculated value of λ is 1.31, which falls within the range of 0.4 to 3.0 and meets the design requirements. This structural and dimensional parameter design allows the vane 40 and roller 30 to form a stable hinge through the multi-arc surface connection part 41 and the arc-shaped connecting groove 31. This optimizes the contact stress distribution at the hinge, avoids problems such as accelerated wear and movement jamming during long-term operation, improves the sealing performance at the mating point of the vane 40 and roller 30, reduces refrigerant leakage in the working chamber 11, reduces frictional power consumption during relative movement, and ensures the reliability and stability of the compressor during long-term operation.

[0028] Please see Figures 3 to 5Furthermore, the connecting part 41 and the connecting groove 31 on the outer wall of the roller 30 are fitted together to form a hinge. The arc surface at the tip of the slide 40 is in inner contact with the arc surface of the connecting groove 31 of the roller 30, which increases the sealing width and can effectively reduce the leakage of high-pressure gas from the gap between the slide 40 and the roller 30. In addition, the hinge structure restricts the slide 40 in the connecting groove 31 of the roller 30, and the two do not separate, eliminating the collision noise of the slide 40 head. The small inner contact radius and the limited rotation of the roller 30 reduce the relative sliding speed between the slide 40 and the roller 30, thereby reducing the frictional power consumption between them.

[0029] Please see Figure 6 Secondly, the connecting part 41 includes at least two arc surfaces, which makes a multi-level gradually changing gap distribution between the tip surface of the slide 40 and the wall of the hinged connecting groove 31 of the roller 30. Compared with a single radius arc, it can store lubricating oil more effectively and form a dynamic pressure oil film during the swinging process, which significantly reduces the coefficient of friction and improves the reliability of the tip of the slide 40.

[0030] Furthermore, this invention defines a parameter λ to characterize the relationship between the key dimensions of the articulated roller 30 and the compressor displacement, and limits its value. When parameter λ is within the range defined by this invention, firstly, the size of the hinge hole of the roller 30 is optimally matched with the inner diameter of the cylinder 10 and the crankshaft eccentricity, effectively controlling the swing angle of the roller and ensuring that the articulated kinematic pair follows the movement throughout the entire operating range, avoiding jamming or sticking of the roller 30; secondly, the thickness of the articulated vane 40 can be optimally matched with the compressor displacement, ensuring the reliability of the vane 40 under extreme operating conditions such as liquid compression and oil compression; in addition, there is room for optimization in the force and lubrication of the connecting part 41 at the tip of the vane 40 and the roller 30, and the side of the vane 40 and the vane groove 12, which can effectively improve the friction loss and wear risk of the vane 40 and improve the mechanical efficiency of the compressor. Further details can be found in the following sections. Figure 9 , Figure 9 To investigate the effect of different λ values ​​on the compressor efficiency (COP) of a 10.8cc displacement model, the test conditions were: speed 30Hz, intake pressure 1.04MPa, and exhaust pressure 2.15MPa.

[0031] The technical solution of the present invention, by hingedly engaging the connecting portion 41, which includes at least two arc surfaces at the end of the sliding vane 40, with the connecting groove 31, which has an arc-shaped main body on the outer surface of the roller 30, and by constraining the λ parameter, which is jointly defined by the diameter of the working cavity 11, the eccentricity of the eccentric portion 21, the diameter of the arc-shaped main body, and the width of the groove of the connecting groove 31, within a range of 0.4 to 3.0, effectively improves the problem of uneven contact stress distribution at the hinge of the sliding vane 40 and the roller 30, avoids accelerated wear or jamming during long-term operation, improves the sealing effect, reduces refrigerant leakage, reduces frictional power consumption, and significantly improves the reliability and working stability of the compressor during long-term operation.

[0032] Please see Figure 6 In one embodiment, the connecting portion 41 includes a first arc segment 411, a second arc segment 412, and a third arc segment 413 connected to each other. The radius of curvature of the second arc segment 412 is different from the radius of curvature of the first arc segment 411 or the third arc segment 413.

[0033] Specifically, the first arc segment 411, the second arc segment 412, and the third arc segment 413 are smoothly connected sequentially along the circumference of the connecting portion 41, together forming the outer circumferential hinged surface of the connecting portion 41. The connecting portion 41 has an overall cylindrical structure and is embedded in the connecting groove 31 of the roller 30. This embodiment uses a composite surface with three arc segments spliced ​​together, so that a multi-level gradual gap is formed between the connecting portion 41 and the inner wall of the connecting groove 31. Compared with a single arc surface, it can store lubricating oil more efficiently and form a multi-level dynamic pressure oil film when the sliding plate 40 and the roller 30 swing relative to each other, fundamentally improving the defect of uneven contact stress distribution. For example, the first arc segment 411 and the third arc segment 413 adopt a small radius of curvature design, and the second arc segment 412 adopts a large radius of curvature design. The three arc segments are smoothly connected without sharp corners, avoiding scratching and wear during operation.

[0034] Please continue reading. Figure 6 Furthermore, the radius of curvature of the second arc segment 412 is greater than that of the first arc segment 411 and the third arc segment 413. Specifically, the first arc segment 411 and the third arc segment 413 are symmetrically distributed on both sides of the second arc segment 412, and the second arc segment 412 is located at the center of the connecting part 41 facing the inner wall of the connecting groove 31. AVL EXCITE lubrication simulation verification shows that when the radius of curvature of the second arc segment 412 is greater than that of the first arc segment 411 and the third arc segment 413 on both sides, the minimum oil film thickness of the hinge gap reaches its peak, and the oil film bearing capacity is optimal.

[0035] This structure creates a wedge-shaped gap, wider in the middle and narrower on both sides, between the connecting part 41 and the connecting groove 31. This generates a "pumping effect" during relative motion, forcing lubricating oil into the friction pair interface and significantly reducing the coefficient of friction. Simultaneously, it evenly distributes the contact stress of the hinge pair, preventing excessive localized stress that could lead to increased wear and jamming. For example, if the radii of curvature of the first arc segment 411 and the third arc segment 413 are set to 1.0 mm, and the radius of curvature of the second arc segment 412 is set to 1.5 mm, the coefficient of friction of the hinge pair can be reduced by more than 40%, effectively extending the compressor's service life.

[0036] Please see Figure 6 and Figure 8In one embodiment, the diameter D2 of the arc-shaped main body is smaller than the thickness T of the slide vane 40. Specifically, the diameter D2 of the arc-shaped main body of the connecting groove 31 is smaller than the thickness T of the slide vane 40. This dimensional relationship facilitates the processing and forming of the connecting portion 41 of the slide vane 40, reduces the manufacturing difficulty of the slide vane 40, and at the same time avoids the arc-shaped main body of the connecting groove 31 being too large, which would weaken the overall structural rigidity of the roller 30, ensure that the roller 30 is not easily deformed during long-term eccentric rotation, and maintain the stability of the compressor operation.

[0037] Please see Figure 8 In one embodiment, the groove width of the connecting groove 31 satisfies 2.0mm ≤ L ≤ 5.5mm. Specifically, the groove opening of the connecting groove 31 is located on the outer peripheral wall of the roller 30, on the side of the arc-shaped main body facing the slide 40. The groove width L can be understood as the minimum width of the groove, or as the line connecting the start and end points of the arc-shaped main body, directly determining the structural strength of the connecting groove 31 and the stability of the hinge fit. When L < 2.0mm, the groove opening of the connecting groove 31 is too narrow, which not only greatly increases the difficulty of CNC machining, but also causes stress concentration at the groove opening position of the roller 30, making it prone to cracking failure under long-term high-load operation; when L > 5.5mm, the opening of the connecting groove 31 is too large, and the connecting part 41 of the slide 40 is prone to detach from the groove opening, causing the hinge structure to fail directly.

[0038] In this embodiment, L is limited to the range of 2.0mm to 5.5mm. For example, conventional machining dimensions such as L=2.0mm, 3.0mm, 4.0mm, 5.0mm, and 5.5mm can be selected. This can ensure the structural strength of the groove opening of the connecting groove 31 and avoid stress cracking. It can also ensure the stable hinge fit between the connecting part 41 and the connecting groove 31 and prevent the slide 40 from separating from the roller 30. At the same time, it is compatible with the machining process of ordinary lathes and grinding machines, reducing the production and manufacturing costs.

[0039] In one embodiment, the roller 30 is made of an alloy material with a Vickers hardness ≥400HV. Specifically, the alloy material can be a chromium-molybdenum-nickel alloy, a high-strength wear-resistant alloy, or other materials with high hardness and high wear resistance. Combined with heat treatment processes such as quenching and tempering, the roller 30 as a whole achieves the mechanical property requirement of a Vickers hardness of not less than 400HV. This material selection and hardness parameter setting can significantly improve the surface wear resistance, structural strength, and impact resistance of the roller 30 connecting groove 31, effectively reducing frictional wear between the sliding vane 40 connecting part 41 and the roller 30 connecting groove 31 during long-term hinged reciprocating motion. This avoids the problem of deformation and accelerated wear of the connecting groove 31 due to insufficient hardness of the roller 30, which could lead to motion jamming. It continuously ensures the accuracy and smoothness of the hinged fit between the sliding vane 40 and the roller 30, further enhancing the reliability and stability of the compressor during long-term operation.

[0040] In one embodiment, the refrigerant used in the compressor is difluoromethane (R32), and the corresponding refrigeration oil is a synthetic ester oil or an ether oil. Specifically, the refrigerant used in the compressor is difluoromethane (R32), and the suitable refrigeration oil is a synthetic ester oil or an ether oil. R32 refrigerant has good compatibility with synthetic ester oil or ether oil, and can form a stable lubricating film at the hinge joint between the sliding vane 40 and the roller 30, effectively reducing friction loss while ensuring lubrication and sealing effects. This adapts to the operating conditions of R32 refrigerant and improves the operating efficiency and stability of the compressor.

[0041] In one embodiment, the refrigerant used in the compressor is a mixture of difluoromethane and pentafluoroethane (R410A), and the corresponding refrigeration oil is a synthetic ester oil or an ether oil. Specifically, the refrigerant used in the compressor is a mixture of difluoromethane and pentafluoroethane (R410A), and the suitable refrigeration oil is a synthetic ester oil or an ether oil. This combination of refrigerant and lubricating oil has excellent compatibility, which can meet the lubrication, sealing, and heat dissipation requirements of the R410A refrigerant compressor, ensure the long-term stable operation of the hinged structure of the vane 40 and roller 30, and maintain the high-efficiency working state of the compressor.

[0042] In one embodiment, the compressor uses propane (R290) as the refrigerant, and the corresponding refrigeration oil is a synthetic ester oil or a polyalkylene glycol oil. Specifically, the compressor uses propane (R290) as the refrigerant, and the suitable refrigeration oil is a synthetic ester oil or a polyalkylene glycol oil. As an environmentally friendly refrigerant, R290, when used in conjunction with synthetic ester oil or polyalkylene glycol oil, can meet the lubrication and sealing requirements of the compressor, adapt to the usage requirements of environmentally friendly refrigeration equipment, ensure the operational reliability of the hinged structure, and improve the overall performance of the compressor.

[0043] The present invention also proposes a refrigeration device, which includes the aforementioned compressor. The specific structure of the compressor is as described in the above embodiments. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0044] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that, include: A cylinder has a working chamber inside, and a sliding vane groove is also provided on the cylinder, which is connected to the working chamber; A crankshaft is disposed within the working cavity, and the crankshaft has an eccentric portion; The roller is sleeved on the eccentric part and is eccentrically rotatable within the working cavity; A slide is reciprocally disposed in the slide groove. The outer surface of the roller is provided with a connecting groove. The connecting groove includes an arc-shaped main body. The end of the slide is provided with a connecting part. The connecting part includes at least two arc surfaces. The connecting part is hinged in the connecting groove. Wherein, the diameter of the working cavity is D1, the eccentricity of the eccentric part is e, the diameter of the arc-shaped main body is D2, and the groove width of the connecting groove is L, satisfying: .

2. The compressor as described in claim 1, characterized in that, The connecting portion includes a first arc segment, a second arc segment, and a third arc segment connected to each other. The radius of curvature of the second arc segment is different from the radius of curvature of the first arc segment or the third arc segment.

3. The compressor as described in claim 2, characterized in that, The radius of curvature of the second arc segment is greater than that of the first arc segment and the third arc segment.

4. The compressor as described in claim 1, characterized in that, The diameter D2 of the arc-shaped main body is smaller than the thickness T of the slider.

5. The compressor as described in claim 1, characterized in that, The width of the connecting groove is 2.0mm≤L≤5.5mm.

6. The compressor as claimed in claim 1, characterized in that, The roller is made of alloy material with a Vickers hardness ≥400HV.

7. The compressor as claimed in claim 1, characterized in that, The compressor uses difluoromethane as the refrigerant and the corresponding refrigeration oil is a synthetic ester oil or an ether oil.

8. The compressor as claimed in claim 1, characterized in that, The compressor uses a mixture of difluoromethane and pentafluoroethane as the refrigerant, and the corresponding refrigeration oil is a synthetic ester oil or an ether oil.

9. The compressor as claimed in claim 1, characterized in that, The compressor uses propane as the refrigerant and the corresponding refrigeration oil is a synthetic ester oil or a polyalkylene glycol oil.

10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 9.

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