Pump body assembly, compressor and refrigeration equipment
By limiting the filling rate η between the vane and the roller and adopting a multi-cylinder segment structure, the hinge fit between the vane and the roller is optimized, solving the balance problem between sealing performance and power consumption, and improving the energy efficiency and reliability of the compressor.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- GUANGDONG MEIZHI COMPRESSOR
- Filing Date
- 2026-04-21
- Publication Date
- 2026-06-12
Smart Images
Figure CN122191081A_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of compressor technology, and in particular to a pump assembly, compressor and refrigeration equipment. Background Technology
[0002] Rotary compressors are widely used in refrigeration equipment such as air conditioners due to their advantages of high efficiency, compact structure, small size, and light weight. The vanes and rollers are the core moving parts of a rotary compressor, and they are usually connected by a hinged structure to achieve the intake, compression, and discharge of the working medium.
[0003] The hinge fit parameters between the vane and the roller directly affect sealing performance and frictional power consumption. If the fit is too loose, it can easily lead to increased gas leakage and decreased volumetric efficiency; if the fit is too tight, it can easily lead to increased frictional power consumption and even cause excessive wear and movement jamming. Currently, the industry lacks a systematic quantitative design benchmark for the hinge fit parameters of this type of hinge structure, making it difficult to achieve a good balance between sealing performance and power consumption, thus restricting further improvements in the overall energy efficiency and operational reliability of the compressor. Summary of the Invention
[0004] The main objective of this application is to propose a pump body assembly that addresses the current technical problem of lacking a systematic quantitative design benchmark for the hinge fit parameters between the vanes and rollers, making it difficult to achieve a good balance between sealing performance and power consumption.
[0005] To achieve the above objectives, the pump body assembly proposed in this application includes: A cylinder has a working chamber inside; the cylinder is also provided with a sliding vane groove, which communicates with the working chamber; A roller is eccentrically rotatably fitted into the working cavity; the outer circumference of the roller is provided with an axially penetrating receiving groove, and the volume of the receiving area formed by the groove surface of the receiving groove and the outer circumference surface of the roller is V1. A sliding structure includes a sliding body and a sliding head; the sliding body is slidably fitted in the sliding groove, and the sliding head is rotatably fitted in the receiving groove; the volume of the portion of the sliding head embedded in the receiving area is V2. .
[0006] In one embodiment, the pump body assembly further includes a crankshaft having an eccentric portion with an eccentricity of e; a roller is sleeved on the eccentric portion; the roller is used to rotate eccentrically along the wall of the working chamber under the drive of the crankshaft; the diameter of the working chamber is D2; The pump body assembly satisfies: .
[0007] In one embodiment, the theoretical displacement of the roller during eccentric rotation is V0; V2 and V0 satisfy the following: .
[0008] In one embodiment, the outer periphery of the slider head has a first cylindrical segment, a second cylindrical segment, and a third cylindrical segment connected sequentially in the circumferential direction; the first cylindrical segment, the second cylindrical segment, and the third cylindrical segment are all arc surfaces.
[0009] In one embodiment, the radius r1 of the first cylindrical segment, the radius r3 of the third cylindrical segment, and the thickness T of the slider body satisfy the following relationship: r1 + r3 < T.
[0010] In one implementation, 0.93 ≤ (r1 + r3) / T < 1.
[0011] In one embodiment, the second cylindrical segment is located between the first cylindrical segment and the third cylindrical segment; the central axis of the first cylindrical segment and the central axis of the third cylindrical segment are collinear, and the radius r1 of the first cylindrical segment is the same as the radius r3 of the third cylindrical segment.
[0012] In one embodiment, the radius r1 of the first cylindrical segment, the radius r2 of the second cylindrical segment, and the radius r3 of the third cylindrical segment satisfy the following relationship: r2 > r1, r2 > r3.
[0013] In one embodiment, the angle between the two ends of the second cylindrical segment and the center of the first cylindrical segment is θ, where 45°≤θ<120°.
[0014] In one embodiment, 45°≤θ≤90°.
[0015] In one embodiment, the groove surface profile of the receiving groove gradually expands outward along the axial direction to form a conical structure.
[0016] In one embodiment, the outer contour of the slider head gradually expands outward along the axial direction to form a tapered structure.
[0017] In one embodiment, the axial taper of the receiving groove is less than or equal to 0.1.
[0018] In one embodiment, the taper of the slider head 42 in the axial direction is less than or equal to 0.1.
[0019] This application also proposes a compressor that includes a pump assembly as described above.
[0020] In one embodiment, the refrigerant used in the compressor is any one of difluoromethane, R410A refrigerant, propane, or R454B refrigerant.
[0021] This application also proposes a refrigeration device, which includes a compressor as described above.
[0022] The pump body assembly proposed in this application limits the filling rate η, which is used to characterize the embedding degree of the vane head in the receiving groove, to a preset value range. This allows the hinge structure formed by the vane head and the receiving groove to achieve both good sealing performance and low friction loss, thereby improving the overall energy efficiency and long-term operational reliability of the compressor while increasing its volumetric efficiency and mechanical efficiency. Attached Figure Description
[0023] To more clearly illustrate the technical solutions in the embodiments of this application 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 this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.
[0024] Figure 1 This is a three-dimensional structural schematic diagram of an embodiment of the pump body assembly provided in this application; Figure 2 A front view of an embodiment of the pump body assembly provided in this application; Figure 3 This is a partial structural schematic diagram of an embodiment of the pump body assembly provided in this application; Figure 4 A schematic diagram of the accommodating area referred to by volume V1 in one embodiment of the pump body assembly provided in this application; Figure 5 A schematic diagram of the embedded portion referred to by volume V2 in one embodiment of the pump body assembly provided in this application; Figure 6 A schematic diagram of the crankshaft structure in one embodiment of the pump body assembly provided in this application; Figure 7 A schematic diagram of the cylinder structure in one embodiment of the pump body assembly provided in this application; Figure 8 A schematic diagram of the overall structure of the roller in one embodiment of the pump body assembly provided in this application; Figure 9 A partial structural schematic diagram of the roller in one embodiment of the pump body assembly provided in this application; Figure 10 A schematic diagram of the structural composition of the receiving tank in one embodiment of the pump body assembly provided in this application; Figure 11A first-view overall structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 12 A second-view overall structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 13 A partial structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 14 A three-dimensional structural schematic diagram of the roller in one embodiment of the pump body assembly provided in this application; Figure 15 This is a three-dimensional structural diagram of the vane structure in one embodiment of the pump body assembly provided in this application.
[0025] Explanation of icon numbers: 1. Cylinder; 11. Working chamber; 12. Sliding vane groove; 2. Crankshaft; 21. Eccentric part; 22. Main shaft; 3. Roller; 31. Receiving groove; 311. First circular arc contour segment; 312. Transition segment; 313. Opening segment; 4. Slider structure; 41. Slider body; 42. Slider head; 43. Avoidance neck; 42a. The second circular arc contour segment; 421. First cylindrical segment; 422. Second cylindrical segment; 423. Third cylindrical segment.
[0026] The realization of the purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation
[0027] The technical solutions of the embodiments of this application 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 this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.
[0028] It should be noted that if the embodiments of this application 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.
[0029] Furthermore, if the embodiments of this application 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. Therefore, 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 that simultaneously satisfies A and B. 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 in this application.
[0030] Rotary compressors are widely used in refrigeration equipment such as air conditioners due to their advantages of high efficiency, compact structure, small size, and light weight. The vanes and rollers are the core moving parts of a rotary compressor, and they are usually connected by a hinged structure to achieve the intake, compression, and discharge of the working medium.
[0031] The hinge fit parameters between the vane and the roller directly affect sealing performance and frictional power consumption. If the fit is too loose, it can easily lead to increased gas leakage and decreased volumetric efficiency; if the fit is too tight, it can easily lead to increased frictional power consumption and even cause excessive wear and movement jamming. Currently, the industry lacks a systematic quantitative design benchmark for the hinge fit parameters of this type of hinge structure, making it difficult to achieve a good balance between sealing performance and power consumption, thus restricting further improvements in the overall energy efficiency and operational reliability of the compressor.
[0032] To address the aforementioned issues, this application proposes a pump body assembly that limits the filling rate η, which characterizes the embedding degree of the vane head in the receiving groove, to a preset value range. This allows the hinge structure formed by the vane head and the receiving groove to achieve both good sealing performance and low frictional loss, thereby improving the overall energy efficiency and long-term operational reliability of the compressor while enhancing its volumetric and mechanical efficiency.
[0033] In all embodiments of this application, the unit for all dimensional parameters (such as length, width, thickness, height, radius, diameter, eccentricity, etc.) is mm, while the unit for displacement is cubic millimeters.
[0034] Please see Figures 1 to 5 The pump assembly provided in this application embodiment includes: The cylinder 1 has a working chamber 11 inside; the cylinder 1 is also provided with a sliding vane groove 12, which extends radially along the working chamber 11 and is connected to the working chamber 11. Roller 3 is eccentrically rotatable within the working cavity 11; the outer circumference of roller 3 is provided with an axially penetrating receiving groove 31; such as Figure 4 As shown, the volume of the receiving area A formed by the groove surface of the receiving groove 31 and the outer circumferential surface of the roller 3 is V1; that is, the volume V1 is bounded by the outer circumferential surface of the roller 3.
[0035] The slider structure 4 includes a slider body 41 and a slider head 42; the slider body 41 is slidably fitted in the slider groove 12, and the slider head 42 is rollably fitted in the receiving groove 31; as shown Figure 5 As shown, the volume of the portion B into which the slider head 42 is embedded in the receiving area A is V2; the filling rate of the slider head 42 in the receiving groove 31 is... , In this context, both V1 and V2 are measured in cubic millimeters.
[0036] In this embodiment, the pump assembly is applied to the compressor. The compressor may include a sealed housing, a motor, etc.; the pump assembly is disposed within the sealed housing; the motor may be a permanent magnet motor to provide driving force.
[0037] The cylinder 1 is roughly ring-shaped, and the internal space of the cylinder 1 forms a cylindrical working chamber 11 with a diameter of D2. The cylinder 1 is also provided with a sliding vane groove 12, which extends radially along the cylinder 1. One end of the sliding vane groove 12 is connected to the working chamber 11, and the other end of the sliding vane groove 12 faces the outside of the cylinder 1.
[0038] The crankshaft 2 has a main shaft 22 and an eccentric part 21 connected to the main shaft 22. The main shaft 22 is connected to the drive part of the motor. The central axis of the main shaft 22 can be coaxially arranged with the central axis of the working chamber 11. The eccentricity of the eccentric part 21 relative to the main shaft 22 is e.
[0039] The roller 3 can be configured as a ring-shaped structure with an outer diameter of D0. The roller 3 is sleeved on the eccentric part 21 of the crankshaft 2. When the crankshaft 2 is driven to rotate by the motor, the eccentric part 21 of the crankshaft 2 can drive the roller 3 to rotate eccentrically within the working cavity 11, that is, to make the central axis of the roller 3 move in a circular motion around the central axis of the working cavity 11, while ensuring that the outer peripheral surface of the roller 3 always maintains contact with or maintains a very small gap from the inner wall surface of the working cavity 11. A receiving groove 31 is provided on the outer peripheral wall of the roller 3. The receiving groove 31 can extend through the axial direction of the roller 3, and the depth direction of the receiving groove 31 is the radial direction of the roller 3. The cross-sectional shape of the receiving groove 31 is an arc shape with the opening facing the cavity wall of the working cavity 11.
[0040] The sliding vane structure 4 includes a vane body 41, a vane head 42, and a clearance neck 43. The two ends of the clearance neck 43 are connected to the vane body 41 and the vane head 42, respectively. The vane body 41 is generally elongated, and its dimension along the axial direction of the roller 3 (i.e., the extension direction of the receiving groove 31) is called the height of the vane body 41. Since the height is consistent throughout the sliding vane structure 4, the height of the vane body 41 is the height H0 of the sliding vane structure 4. The dimension of the vane body 41 along the width of the vane groove 12 (i.e., along the circumference of the cylinder 1) is called the thickness T of the vane body 41. The height of the vane body 41 (i.e., the height H of the sliding vane structure 4) and the thickness T of the vane body 41 are matched with the vane groove 12, allowing the vane body 41 to smoothly reciprocate along the extension direction of the vane groove 12 (i.e., the radial direction of the cylinder 1). The end of the vane body 41 facing the roller 3 is connected to the vane head 42 via the clearance neck 43. The slide head 42 has a columnar structure, the axis of which is parallel to the height direction of the slide body 41 and the axis of which is parallel to the axis of the roller 3. The slide head 42 is hinged in the receiving groove 31 so that the slide structure 4 and the roller 3 are connected, and the slide head 42 can roll relative to the receiving groove 31 in its circumferential direction. The length of the clearance neck 43 in the extension direction of the slide groove 12 (i.e., the radial direction of the cylinder 1) is L2; the minimum width of the clearance neck 43 is B3, which is less than the thickness T of the slide body 41 and the diameter d1 of the slide head 42; where d1 is the minimum circumscribed circle diameter of the slide head 42. Both sides of the groove opening of the receiving groove 31 extend inward to form a groove limiting part that matches the clearance neck 43, so as to prevent the slide head 42 from disengaging from the receiving groove 31. The total length of the sliding vane structure 4 in the extending direction of the sliding vane groove 12 (i.e., the radial direction of the cylinder 1) is Lv.
[0041] Roller 3 and vane structure 4 together divide the working chamber 11 into an intake chamber and a compression chamber. The intake chamber is connected to the intake port on one side of cylinder 1, and the compression chamber is connected to the exhaust port on the other side of cylinder 1. During the process of the motor driving roller 3 to rotate eccentrically within the working chamber 11 via crankshaft 2, vane structure 4 is driven by roller 3 to reciprocate linearly in vane groove 12. During this process, vane head 42 also rolls relative to receiving groove 31 to adapt to changes in the relative angle between roller 3 and vane structure 4. Based on the above-described actions of roller 3 and vane structure 4, the compressor's working medium can enter the intake chamber from the intake port under negative pressure. The working medium entering the intake chamber will gradually transfer to the exhaust chamber as roller 3 rotates. The working medium entering the exhaust chamber can be compressed into a high-temperature, high-pressure gas and finally discharged from the exhaust port, thus completing one working cycle. In one working cycle, the total amount of gas discharged through the eccentric rotation of roller 3 relative to cylinder 1 can be called the theoretical displacement V0 of the pump assembly. The theoretical displacement V0 can also be characterized by the gas volume obtained by subtracting the volume occupied by roller 3 from the total volume of working chamber 11. The unit of theoretical displacement V is cubic millimeters. It should be noted that the theoretical displacement V0 is for a single cylinder 1; when the compressor is a twin-cylinder compressor or a multi-cylinder compressor, the theoretical displacement V0 is the displacement corresponding to one cylinder 1 in the compressor.
[0042] Based on the aforementioned hinged connection between the slider head 42 and the receiving groove 31, a certain clearance needs to be maintained between the slider head 42 and the receiving groove 31 to ensure smooth relative movement. The size of this clearance directly affects the sealing performance and frictional power consumption of the hinged structure. Furthermore, the size of this clearance is related to the volume of the slider head 42 embedded in the receiving groove 31 (i.e., the filling rate of the slider head 42 in the receiving groove 31): the larger the volume ratio of the slider head 42 embedded in the receiving groove 31 (i.e., the higher the filling rate), the smaller the effective clearance between them; conversely, the smaller the volume ratio of the slider head 42 embedded in the receiving groove 31 (i.e., the lower the filling rate), the larger the effective clearance between them. Therefore, based on the above considerations, this embodiment adopts a volume filling rate... To characterize the degree of embedding of the slider head 42 in the receiving groove 31, such as Figure 4 As shown, the volume of the receiving area A formed by the groove surface of the receiving groove 31 and the outer circumferential surface of the roller 3 is V1, that is, the volume V1 is bounded by the outer circumferential surface of the roller 3; as shown Figure 5 As shown, the volume of part B embedded in the receiving area A by the slider head 42 is V2.
[0043] It is understandable that volumes V1 and V2 can be obtained through calculation or by measurement using appropriate detection devices; no limitation is made here.
[0044] Experiments have verified that when the above fill rate η satisfies In this case, the hinge structure formed by the vane head 42 and the receiving groove 31 can achieve a good balance between sealing performance and friction loss. Specifically, when η < 0.85, the vane head 42 is not embedded enough in the receiving groove 31, the clearance between them is too large, and the sealing performance is insufficient. This causes high-pressure side gas to easily leak to the low-pressure side through the clearance, resulting in a significant decrease in the volumetric efficiency of the compressor. When η > 0.93, the vane head 42 is embedded too much in the receiving groove 31, and the clearance between them is too small. Although this improves the sealing performance, the frictional resistance between the vane head 42 and the receiving groove 31 will increase significantly, leading to increased mechanical friction power consumption and thus reducing the overall energy efficiency of the compressor. In addition, the excessively small clearance will also adversely affect the entry of lubricating oil and the formation of oil film. In the case of insufficient lubrication, excessive wear is likely to occur at the contact interface, which will further reduce the long-term operational reliability of the compressor.
[0045] Therefore, by limiting the filling rate η to the range of 0.85 to 0.93, this embodiment can ensure that the hinge structure formed by the vane head 42 and the receiving groove 31 has both good sealing performance and low friction loss. This can improve the volumetric efficiency and mechanical efficiency of the compressor, as well as its overall energy efficiency and long-term operational reliability.
[0046] In one embodiment, refer to Figures 1 to 5 The cross-sectional area S1 of the receiving groove 31 (bounded by the outer circumferential surface of the roller 3) remains constant in the axial direction, and the cross-sectional area S2 of the portion B of the sliding head 42 embedded in the receiving area A remains constant in the axial direction; filling rate .
[0047] In practical applications, the height of the roller 3 in the extension direction of the receiving groove 31 is usually equal to the height of the sliding structure 4 in the extension direction of the receiving groove 31, and both can be represented by H0.
[0048] When the axial cross-sectional area of the receiving groove 31 remains constant, and the axial cross-sectional area of the portion B of the sliding head 42 embedded in the receiving area A also remains constant, the volume V1 is equal to the product of its cross-sectional area S1 and its height H0, and the volume V2 is equal to the product of its cross-sectional area S2 and its height H0. In this case, the filling rate η = V2 / V1 = (S2*H0) / (S1*H0) = S2 / S1. Therefore, under the condition of a constant cross-section, the filling rate η can be directly calculated using the ratio of the cross-sectional areas, making the calculation more convenient.
[0049] Specifically, the cross-sectional area S1 of the receiving groove 31 can be calculated using the following formula: Reference Figures 2 to 13The roller 3 is annular, with an outer diameter of D0 and a center distance of L0 between the receiving groove 31 and the inner ring of the roller 3. like Figure 9 and Figure 10 As shown, the cross-sectional shape of the receiving groove 31 includes a first arc profile segment 311, a transition segment 312, and an opening segment 313 connected sequentially in a radially outward direction; the first arc profile segment 311 has an outward-facing arc shape, the diameter of the first arc profile segment 311 is D1, and the cross-sectional area occupied by the first arc profile segment 311 is C; the width B1 of the transition segment 312 is less than D1, the radial length of the transition segment 312 is L1, the central angle corresponding to the transition segment 312 on the first arc profile segment 311 is β, and the cross-sectional area occupied by the transition segment 312 is D; the width of the opening segment 313 gradually increases from the inside to the outside, the maximum width of the opening segment 313 is B2, and the cross-sectional area occupied by the opening segment 313 is E. The cross-sectional area S1 of the receiving groove 31 satisfies: + L1+( .
[0050] Similarly, the cross-sectional area S2 of the portion B embedded in the receiving area A of the slider head 42 can be calculated using the following formula: Reference Figures 2 to 13 The slider structure 4 also includes an avoidance neck 43, which connects the slider body 41 and the slider head 42; the slider body 41 is slidably fitted in the slider groove 12; The diameter of the slider head 42 is d1, the minimum width of the clearance neck 43 is B3, and the length of the clearance neck 43 is L2; the slider head 42 forms a second arc profile segment 42a on the cross-section of the slider structure 4, and the central angle corresponding to the clearance neck 43 on the second arc profile segment 42a is α. The cross-sectional area S2 satisfies: .
[0051] Based on this, the volume V2 of the portion B embedded in the receiving area A by the slider head 42 can be calculated using the following formula: ).
[0052] In one embodiment, refer to Figures 2 to 13 The pump body assembly also includes a crankshaft 2, which has an eccentric part 21 with an eccentricity of e; a roller 3 is sleeved on the eccentric part 21; the roller 3 is used to rotate eccentrically along the cavity wall of the working cavity 11 under the drive of the crankshaft 2. The working chamber 11 is cylindrical, and the diameter of the working chamber 11 is D2; The pump body assembly meets the following requirements (the units of B1, D1, D2, and e are all in mm): .
[0053] Specifically, the numerator of the above formula mainly reflects the opening characteristics of the receiving groove 31 and the size parameters of the vane head 42; the denominator is related to the diameter D2 of the working chamber 11 and the eccentricity e of the crankshaft 2, which can be used to characterize the displacement level and motion amplitude of the pump body assembly.
[0054] Experiments have shown that when the ratio is less than 0.4, it indicates that the size of the receiving groove 31 is too small relative to the displacement of the pump body assembly. In this case, the load-bearing capacity of the hinge structure is insufficient, and it is prone to deformation or damage under high load conditions, posing a high reliability risk. When the ratio is greater than 3, it indicates that the size of the receiving groove 31 is too large relative to the displacement of the pump body assembly. In this case, the fit clearance between the receiving groove 31 and the vane head 42 is too large, resulting in insufficient sealing performance. This can easily lead to leakage of gas in the high-pressure area through the fit clearance, thereby reducing the volumetric efficiency of the compressor.
[0055] Therefore, this embodiment limits the above ratio to a range of 0.4 to 3, which allows the size of the receiving groove 31 to match the displacement level and movement range of the pump body assembly. This ensures the load-bearing reliability of the hinge structure while effectively controlling the risk of leakage, thus balancing the high-efficiency operation and long-term reliability of the large-displacement compressor.
[0056] In one embodiment, refer to Figures 2 to 13 The theoretical displacement of roller 3 when it rotates eccentrically is V0; the volume V2 and the theoretical displacement V0 satisfy the following relationship (the units of V2 and V0 are both cubic millimeters): .
[0057] Specifically, the aforementioned ratio reflects the degree of matching between the volume ratio of the articulated structure and the displacement of the pump assembly. Experiments have verified that when V2 / V0 is less than 1.35%, the load-bearing capacity of the articulated structure is too weak relative to the current displacement, making it prone to deformation and failure during operation. Conversely, when V2 / V0 is greater than 1.75%, the articulated structure is too large relative to the current displacement, increasing inertia and frictional losses, which is detrimental to energy efficiency. Therefore, by limiting the ratio to the range of 1.35% to 1.75%, the dimensions of the articulated structure can be matched with the current displacement of the pump assembly, thus balancing load-bearing reliability and overall machine energy efficiency.
[0058] In one embodiment, refer to Figures 2 to 13 The working cavity 11 is cylindrical and has a diameter of D2; the roller 3 is annular and has an outer diameter of D0; the height of the roller 3 and the height of the sliding structure 4 are both H0. The theoretical displacement V0, the diameter D2 of the working chamber 11, and the outer diameters D0 and H0 of the roller 3 satisfy the following: .
[0059] Specifically, when the roller 3 rotates eccentrically within the working chamber 11, a crescent-shaped region is formed between the outer circumferential surface of the roller 3 and the wall of the working chamber 11. The volume of this crescent-shaped region can characterize the total amount of gas discharged by the pump assembly in one complete working cycle (i.e., the roller 3 rotates eccentrically one revolution relative to the working chamber 11), which is also the theoretical displacement V0. Thus, the theoretical displacement V0 can be obtained by calculating the volume of this crescent-shaped region.
[0060] In practical applications, since the height of cylinder 1 (i.e., the height of the cylindrical region corresponding to working cavity 11), the height of roller 3 (i.e., the height of the cylinder corresponding to roller 3), and the height of sliding vane structure 4 are the same, all three can be represented by height H0. The volume of the cylindrical region corresponding to working cavity 11 can be calculated using height H0, and the volume of the cylinder corresponding to roller 3 can also be calculated using height H0. Specifically, the volume of the cylindrical region corresponding to working cavity 11 is... The volume of the cylinder corresponding to roller 3 is Then, by subtracting the volume of the cylinder corresponding to the roller 3 from the volume of the cylindrical region corresponding to the working cavity 11, the volume of the crescent-shaped region formed between the working cavity 11 and the roller 3 can be obtained. The volume of this crescent-shaped region is the theoretical displacement V0, which can then be substituted into the above embodiment. This relationship is used for calculation.
[0061] In one embodiment, refer to Figure 11 and Figure 13 The outer periphery of the slider head 42 has a first cylindrical section 421, a second cylindrical section 422 and a third cylindrical section 423 connected in sequence along the circumference; the first cylindrical section 421, the second cylindrical section 422 and the third cylindrical section 423 are all arc surfaces.
[0062] Compared to the existing technology where the outer peripheral surface of the vane head 42 is a single arc surface, this embodiment uses a three-cylindrical segment design, which provides more degrees of freedom for adjusting the shape of the outer peripheral surface of the vane head 42. Specifically, designers can flexibly design the radius of curvature or plane angle of each cylindrical segment, as well as the relative position and connection method between the cylindrical segments, according to the compressor's operating parameters, such as the pressure of the working medium, the speed range, and the lubrication conditions. This allows the contact area, contact pressure distribution, and contact gap between the vane head 42 and the receiving groove 31 to be finely configured according to actual needs.
[0063] When the vane head 42 engages with the receiving groove 31, the vane structure 4 can oscillate relative to the roller 3 within a certain angular range. During a complete cycle of compressor operation, the relative position between the roller 3 and the vane structure 4 continuously changes; during this process, multiple cylindrical sections of the vane head 42 can sequentially contact the groove surface of the receiving groove 31. By rationally setting the geometric parameters of each cylindrical section, the contact stress can be distributed more evenly on the surface of the vane head 42, avoiding excessively high local stress peaks. Simultaneously, the naturally formed micro-gaps or oil wedge regions between the multiple cylindrical sections and the groove surface of the receiving groove 31 facilitate the storage and flow of lubricating oil, promoting the formation of a hydrodynamic oil film, thereby reducing the coefficient of friction and wear rate.
[0064] As can be seen, in this embodiment, the outer peripheral surface of the slide head 42 is set to have three cylindrical segments connected in sequence along the circumference. This changes the original single contour shape of the slide head 42, thereby providing a structural basis for the adjustment of the inherent mating relationship and operating parameters. This makes it possible to further improve the contact characteristics, stress distribution, wear degree and lubrication performance, which were originally difficult to optimize in depth due to the single contour shape.
[0065] In one embodiment, refer to Figure 11 and Figure 13 The radius r1 of the first cylindrical segment 421, the radius r3 of the third cylindrical segment 423, and the thickness T of the slider body 41 satisfy the following relationship: r1 + r3 < T. Here, the units of r1, r3, and T are all mm.
[0066] In this embodiment, the first cylindrical segment 421 and the third cylindrical segment 423 can be distributed on both sides of the slider head 42; the sum of the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 can be used to characterize the size of the slider head 42 in the thickness direction of the slider body 41. By limiting r1+r3<T, the overall machinability of the slider structure 4 can be improved, and the problem of material waste and reduced processing efficiency caused by the need to reserve additional blank material for the slider head 42 due to the size of the slider head 42 being larger than the thickness T of the slider body 41 can be avoided.
[0067] In one embodiment, refer to Figure 11 and Figure 13 0.93≤(r1+r3) / T<1; In this way, the difference between the size of the slider head 42 and the thickness T of the slider body 41 can be controlled within a small range, thereby avoiding the problem of material waste and long processing time caused by excessive size difference, and avoiding the adverse effects on the structural strength, rigidity, and load-bearing capacity of the slider head 42 due to the size being too small relative to the slider body 41.
[0068] In one embodiment, refer to Figure 11 and Figure 13 The second cylindrical segment 422 is located between the first cylindrical segment 421 and the third cylindrical segment 423; the central axis of the first cylindrical segment 422 and the central axis of the third cylindrical segment 423 are collinear, and the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 are the same.
[0069] In this embodiment, the first cylindrical segment 421 and the third cylindrical segment 423 can be distributed on both sides of the slider head 42; in such cases... Figure 11 and Figure 13 In the cross-sectional view shown, when the center of the first cylindrical segment 421 and the center of the third cylindrical segment 423 are set concentrically, the center of both the first cylindrical segment 421 and the third cylindrical segment 423 can be the center of the slider head 42.
[0070] Based on the concentric arrangement and equal radius of the first cylindrical segment 421 and the third cylindrical segment 423, the two arc-shaped cylindrical segments form symmetrical bearing areas on the outer circumference of the slider head 42. When the slider head 42 rolls into the receiving groove 31, the first cylindrical segment 421 and the third cylindrical segment 423 can respectively contact the two side walls of the receiving groove 31, thus providing a balanced support force and helping to form a stable and uniform support area in the receiving groove 31. This is beneficial to improving the positioning stability and smooth movement of the slider head 42 in the receiving groove 31.
[0071] It should be noted that the requirement that the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 be the same allows for manufacturing tolerances, and does not require that the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 be exactly equal in actual value; specifically, r1 and r3 can have a tolerance of ±0.008mm.
[0072] In one embodiment, refer to Figure 11 and Figure 13 The radii r1 of the first cylindrical segment 421, r2 of the second cylindrical segment 422, and r3 of the third cylindrical segment 423 satisfy the following relationship: r2 > r1, r2 > r3. The units of r1, r2, and r3 are all mm.
[0073] In this embodiment, the curvature of the second cylindrical segment 422 is less than that of the first cylindrical segment 421 and the third cylindrical segment 423; thus, the gap between the second cylindrical segment 422 and the receiving groove 31 is greater than the gap between the first cylindrical segment 421 and the third cylindrical segment 423 and the receiving groove 31. Based on the above structural configuration, when the sliding head 42 moves relative to the receiving groove 31, a gradually changing wedge-shaped gap can be formed between the sliding head 42 and the groove surface of the receiving groove 31; the volume change of this wedge-shaped gap can generate a pumping effect on the lubricating oil, which can force the lubricating oil into the friction interface, thereby building a stable lubricating oil film in the contact area between the sliding head 42 and the receiving groove 31. This can improve the quality of the oil film, thereby enhancing the lubrication effect, reducing friction and wear, and further improving the reliability and service life of the hinged fit between the sliding head 42 and the receiving groove 31.
[0074] In one embodiment, refer to Figure 11 and Figure 13 The angle between the two ends of the second cylindrical segment 422 and the center of the first cylindrical segment 421 is θ, where 45°≤θ<120°.
[0075] like Figure 13 As shown, under the premise that the first cylindrical segment 421 and the third cylindrical segment 423 are concentric and have the same radius, the center of circle A1 where the first cylindrical segment 421 and the third cylindrical segment 423 are located is O1, the center of circle A2 where the second cylindrical segment 422 is located is O2, and the angle formed by the lines connecting the two ends of the second cylindrical segment 422 and the center O1 is θ.
[0076] Specifically, when the included angle θ is too small (θ < 45°), the circumferential extension length of the wedge-shaped gap in the above embodiment will be insufficient, making it difficult to form an effective pumping effect on the lubricating oil. This results in limited establishment and maintenance of the lubricating oil film and insignificant lubrication improvement. Conversely, when the included angle θ is too large (θ ≥ 120°), the second cylindrical section 422 will excessively encroach on the contact area between the slide head 42 and the receiving groove 31, reducing the effective bearing area of the first cylindrical section 421 and the third cylindrical section 423. This increases the contact surface pressure, which in turn exacerbates friction and wear, reducing the reliability of the fit between the slide head 42 and the receiving groove 31. Therefore, this embodiment limits the included angle θ to 45° ≤ θ < 120°, ensuring that the slide head 42 has sufficient bearing area while maintaining good lubrication, thus balancing the lubrication performance and bearing reliability of the hinged part.
[0077] In one embodiment, refer to Figure 11 and Figure 1345°≤θ≤90°. By further limiting the maximum value of θ (θ not greater than 90°), the problem of excessively changing the shape and structure of the slider head 42 and the fit between the slider head 42 and the receiving groove 31 due to the excessive coverage of the second cylindrical segment 422 can be avoided, thereby reducing the accuracy of the characterization of the filling rate η.
[0078] In one embodiment, refer to Figure 14 and Figure 15 and supplementary reference Figure 4 and Figure 5 The groove surface of the receiving groove 31 gradually expands outward along the axial direction to form a conical structure; the outer contour of the slider head 42 gradually expands outward along the axial direction to form a conical structure. The height of the roller 3 and the height of the slider structure 4 are both H0; Volume V1 satisfies: Among them, such as Figure 4 As shown, The cross-sectional area of the receiving area A formed by the groove surface of the receiving groove 31 and the outer circumferential surface of the roller 3 on the reference cross-section is H. The reference cross-section is any cross-section between the two ends of the receiving groove 31, and the distance between the reference cross-section and the reference end face of the roller 3 is H. Volume V2 satisfies: Among them, such as Figure 5 As shown, The cross-sectional area of portion B of the sliding head 42 embedded in the receiving area A on the aforementioned reference cross-section.
[0079] In this embodiment, both the receiving groove 31 and the slider head 42 are configured with a variable cross-section structure along the axial direction. When the slider head 42 is hinged in the receiving groove 31, the end with a larger cross-sectional area on the slider head 42 is correspondingly set to the end with a larger cross-sectional area on the receiving groove 31, and the end with a smaller cross-sectional area on the slider head 42 is correspondingly set to the end with a smaller cross-sectional area on the receiving groove 31.
[0080] Based on the above-mentioned variable cross-section structure and corresponding fit, the adaptability of the hinge structure to different application scenarios can be improved; at the same time, the variable cross-section structure can form a certain taper fit in the axial direction, thereby playing a relative positioning role in the axial direction, which helps to suppress the axial displacement of the sliding plate structure 4 relative to the receiving groove 31, thereby improving the operational stability.
[0081] When using the above-mentioned variable cross-section structure, the volumes V1 and V2 need to be calculated using the above integral formula in order to accurately obtain the filling rate η of the hinged structure under the variable cross-section condition, thereby providing a precise design basis for the performance optimization of the pump body components.
[0082] In one embodiment, refer to Figure 14 and Figure 15The taper of the receiving groove 31 in the axial direction is less than or equal to 0.1.
[0083] In one embodiment, refer to Figure 14 and Figure 15 The taper of the slider head 42 in the axial direction is less than or equal to 0.1.
[0084] Specifically, when both the receiving groove 31 and the sliding head 42 adopt a variable cross-section structure, the receiving groove 31 and the sliding head 42 can form a certain taper in the axial direction. If the taper is too large, it may hinder the rolling action of the sliding head 42 in the receiving groove 31, or even cause problems such as jamming and uneven wear.
[0085] Based on the above considerations, this embodiment limits the taper of the receiving groove 31 and the taper of the sliding head 42 to less than or equal to 0.1. This allows for the implementation of a variable cross-section structure while avoiding adverse effects on the normal rolling fit of the hinge mechanism. The taper can be calculated by multiplying the difference between the cross-sectional area of the large end and the cross-sectional area of the small end by the height H0.
[0086] This application also provides a compressor; please refer to [link / reference]. Figures 1 to 15 The compressor includes the pump assembly in any of the above embodiments.
[0087] In this embodiment, the compressor specifically includes a pump body assembly and other necessary components that work in conjunction with it, which are not listed here. For the specific structure of the pump body assembly, please refer to the description of the above embodiments. Since the compressor in this embodiment adopts all the technical solutions of all the above embodiments, it possesses at least all the beneficial effects brought about by the technical solutions of the above embodiments. That is, by limiting the filling rate η, which characterizes the embedding degree of the vane head 42 in the receiving groove 31, to a preset value range, the hinge structure formed by the vane head 42 and the receiving groove 31 can achieve both good sealing performance and low frictional loss. This improves the compressor's volumetric efficiency and mechanical efficiency while enhancing its overall energy efficiency and long-term operational reliability.
[0088] Furthermore, the refrigerant used in the compressor is any one of difluoromethane (R32 refrigerant), R410A refrigerant, propane (R290 refrigerant), or R454B refrigerant.
[0089] This application also provides a refrigeration device; please refer to [link / reference]. Figures 1 to 15 The refrigeration equipment includes the compressor in any of the above embodiments.
[0090] The refrigeration equipment in this embodiment may include air conditioners, refrigerators, etc., and is not limited here.
[0091] For other specific structural details of the compressor, please refer to the description of the above embodiments. Since the refrigeration equipment in this embodiment employs all the technical solutions of all the above embodiments, it possesses at least all the beneficial effects brought about by the technical solutions of the above embodiments, and will not be repeated here.
[0092] The above description is merely an exemplary embodiment of this application and does not limit the patent scope of this application. Any equivalent structural transformations made based on the technical concept of this application and the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this application.
Claims
1. A pump body assembly, characterized in that, include: A cylinder has a working chamber inside; the cylinder is also provided with a sliding vane groove, which communicates with the working chamber; A roller is eccentrically rotatably fitted into the working cavity; the outer circumference of the roller is provided with an axially penetrating receiving groove, and the volume of the receiving area formed by the groove surface of the receiving groove and the outer circumference surface of the roller is V1. A sliding plate structure includes a sliding plate body and a sliding plate head; the sliding plate body is slidably engaged in the sliding plate groove, and the sliding plate head is rotatably engaged in the receiving groove; The volume of the portion of the slider head embedded in the receiving area is V2; .
2. The pump body assembly according to claim 1, characterized in that, The pump body assembly also includes a crankshaft having an eccentric portion with an eccentricity of e; a roller is sleeved on the eccentric portion; the roller is used to rotate eccentrically along the wall of the working chamber under the drive of the crankshaft; the diameter of the working chamber is D2. The pump body assembly satisfies: 。 3. The pump body assembly according to claim 1, characterized in that, The theoretical displacement of the roller during eccentric rotation is V0; V2 and V0 satisfy the following: 。 4. The pump body assembly according to claim 1, characterized in that, The outer periphery of the slider head has a first cylindrical section, a second cylindrical section, and a third cylindrical section connected sequentially in the circumferential direction; the first cylindrical section, the second cylindrical section, and the third cylindrical section are all arc surfaces.
5. The pump body assembly according to claim 4, characterized in that, The radius r1 of the first cylindrical segment, the radius r3 of the third cylindrical segment, and the thickness T of the slider body satisfy the following relationship: r1 + r3 < T.
6. The pump body assembly according to claim 5, characterized in that, 0.93≤（r1+r3） / T＜1。 7. The pump body assembly according to claim 5, characterized in that, The second cylindrical segment is located between the first cylindrical segment and the third cylindrical segment; the central axis of the first cylindrical segment and the central axis of the third cylindrical segment are collinear, and the radius r1 of the first cylindrical segment and the radius r3 of the third cylindrical segment are the same.
8. The pump body assembly according to claim 7, characterized in that, The radius r1 of the first cylindrical segment, the radius r2 of the second cylindrical segment, and the radius r3 of the third cylindrical segment satisfy the following relationship: r2 > r1, r2 > r3.
9. The pump body assembly according to claim 8, characterized in that, The angle between the two ends of the second cylindrical segment and the center of the first cylindrical segment is θ, where 45°≤θ<120°.
10. The pump body assembly according to claim 9, characterized in that, 45°≤θ≤90°.
11. The pump body assembly according to any one of claims 1 to 10, characterized in that, The contour of the receiving groove gradually expands outward along the axial direction to form a conical structure; And / or, the outer contour of the slider head gradually expands outward along the axial direction to form a tapered structure.
12. The pump body assembly according to claim 11, characterized in that, The taper of the receiving groove in the axial direction is less than or equal to 0.1; And / or, the taper of the slider head in the axial direction is less than or equal to 0.
1.
13. A compressor, characterized in that, The compressor includes a pump body assembly as described in any one of claims 1 to 12.
14. The compressor according to claim 13, characterized in that, The compressor uses any one of the following refrigerants: difluoromethane, R410A refrigerant, propane, or R454B refrigerant.
15. A refrigeration device, characterized in that, The refrigeration equipment includes a compressor as described in any one of claims 13 to 14.