Pump body assembly and compressor with same

Abstract

The invention provides a pump body structure and a compressor with the same, the pump body structure comprises a crankshaft assembly and a lower flange, the pump body structure further comprises a flow guide part arranged on the lower flange, and the flow guide part is used for storing lubricating liquid so as to lubricate the contact surface, making contact with the lower flange, of the crankshaft assembly through the lubricating liquid; the flow guide part extends along a preset curve track, and the extending direction is the same as the rotating direction of the crankshaft assembly. The problems that in the prior art, abrasion is likely to be generated between a lower flange and a roller and between the lower flange and a crankshaft, and the service life and the operation energy efficiency of a compressor are adversely affected are solved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular, to a pump body structure and a compressor having the same. Background Art

[0002] A rolling rotor compressor mainly consists of two major components: a pump body and an electric motor. Among them, the pump body assembly mainly includes a cylinder, a crankshaft, a roller, a sliding vane, and upper and lower flanges. The pump body crankshaft is in interference fit with the electric motor rotor. The R-shaped end face of the sliding vane is in line contact and abuts against the outer cylindrical surface of the roller under the action of spring force and the back pressure inside the shell, thereby dividing the internal volume formed by the cylinder and the roller into two crescent-shaped suction chambers and compression chambers. Its working principle is that the crankshaft rotates periodically under the driving force of the electric motor, and drives the roller to rotate eccentrically synchronously through its eccentric structure, and then drives the sliding vane to perform radial reciprocating motion in the sliding vane groove of the cylinder, so that the volumes of the suction chamber and the compression chamber change accordingly, thereby realizing the periodic suction, compression, and exhaust processes of the compressor.

[0003] During the operation of the compressor, the eccentric part of the crankshaft drives the roller to rotate synchronously. The lower thrust surface of the eccentric circle of the crankshaft and the lower end surface of the roller are in contact with the large end surface of the lower flange and have a relatively large area of relative movement, which is one of the wear forms with a relatively high proportion in the rotary compressor. Especially when some of the parts are replaced with ceramic materials (such as the roller), due to the influence of the surface quality and hardness characteristics of the ceramic material, the wear will be further increased, which has an adverse effect on the service life and operating energy efficiency of the compressor. Summary of the Invention

[0004] The main object of the present invention is to provide a pump body structure and a compressor having the same, so as to solve the problem in the prior art that wear is likely to occur between the lower flange and the roller and the crankshaft, which has an adverse effect on the service life and operating energy efficiency of the compressor.

[0005] To achieve the above object, according to one aspect of the present invention, a pump body structure is provided, which includes a crankshaft assembly and a lower flange. The pump body structure further includes: a diversion part, which is arranged on the lower flange and is used to store lubricating liquid inside to lubricate the contact surface where the crankshaft assembly contacts the lower flange through the lubricating liquid; wherein, the diversion part extends along a predetermined curve trajectory, and the extending direction is the same as the rotation direction of the crankshaft assembly.

[0006] Furthermore, the lower flange further includes a through channel, at least a part of the crankshaft assembly is arranged in the through channel, and the through channel is communicated with the oil outlet hole of the crankshaft assembly; one end of the diversion part is communicated with the through channel, and the other end extends along the rotation direction of the crankshaft assembly, and the lubricating oil in the oil outlet hole flows into the diversion part after flowing through the through channel.

[0007] Further, the pump body structure further includes a sliding vane. The guiding portion includes a first end portion and a second end portion which are oppositely arranged. The first end portion is communicated with the penetrating channel. The included angle between the plane where the center line of the first end portion is located and the sliding vane is θ1, and θ1 > 200°; the included angle between the plane where the end face of the second end portion is located and the sliding vane is θ2, and θ2 ≤ 330°.

[0008] Further, the guiding portion includes: a first guiding section and a second guiding section which are communicated with each other. The first guiding section is communicated with the penetrating channel and extends along a first arc track. The second guiding section extends along a second arc track.

[0009] Further, the second guiding section includes a first arc surface and a second arc surface which are opposite and spaced apart. A guiding space for guiding lubricating oil is arranged between the first arc surface and the second arc surface. The first arc surface is arranged closer to the penetrating channel than the second arc surface. The crankshaft assembly includes a thrust surface which fits with the lower flange; the radius of the circle where the thrust surface is located is R1, the inner radius of the penetrating channel is R4, the radius of the circle where the second arc surface is located is R2, and the radius of the circle where the first arc surface is located is R3; wherein, R1 - R2 ≥ 2 mm; R3 - R4 ≥ 2 mm.

[0010] Further, the lower flange includes a fitting end face which fits with the crankshaft assembly. At least part of the guiding portion is arranged on the fitting end face. The guiding portion includes: a guiding groove, and the extending direction of the guiding groove is the same as the rotating direction of the crankshaft assembly.

[0011] Further, the width of the guiding groove is T, and the depth is H, wherein, 1 mm ≤ T ≤ 3 mm, and H ≤ 2.5 mm.

[0012] Further, a penetrating channel for the crankshaft assembly to pass through is arranged on the lower flange. The guiding groove includes: a main groove body, one end of the main groove body is communicated with the penetrating channel, and the other end extends along the rotating direction of the crankshaft assembly; a sub - flow groove body, which is communicated with the main groove body, and there are a plurality of sub - flow groove bodies which are arranged at intervals along the extending direction of the main groove body.

[0013] Further, the width of the main groove body is T, and the width of the sub - flow groove body is T1.

[0014] Wherein, T1 = (0.5 - 0.8)T.

[0015] Further, the pump body structure further includes: a cylinder, which is sleeved on the crankshaft assembly. The cylinder includes an air inlet cavity and an air outlet cavity. The guiding portion is oppositely arranged with the air outlet cavity.

[0016] According to another aspect of the present invention, a compressor is provided, which includes a machine body and a pump body structure. The pump body structure is arranged in the machine body, and the pump body structure is the above - mentioned pump body structure.

[0017] Applying the technical solution of the present invention, the pump body structure includes a crankshaft assembly, a lower flange, and a diversion part. The diversion part is arranged on the lower flange and is used to store lubricating fluid, and lubricate the contact surface where the crankshaft assembly contacts the lower flange through the lubricating fluid; wherein, the diversion part extends along a predetermined curve trajectory, and the extension direction is the same as the rotation direction of the crankshaft assembly. With such a setting, during the rotation of the crankshaft assembly, when it periodically contacts the lower flange, the lubricating fluid stored in the diversion part can be used for lubrication, avoiding the problem that the friction force between the crankshaft and the lower flange is too large, thereby affecting the service life of the pump body structure and the operating energy efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The schematic diagrams in the specification forming a part of this application are used to provide a further understanding of the present invention. The schematic embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation to the present invention. In the drawings:

[0019] Figure 1 shows a schematic structural diagram of a pump body structure in the prior art;

[0020] Figure 2 shows a schematic structural diagram of the crankshaft assembly of the pump body structure according to the present invention;

[0021] Figure 3 shows a cross-sectional view of the schematic structural diagram of the pump body structure according to the present invention;

[0022] Figure 4 shows a schematic structural diagram of the crankshaft assembly in the pump body structure according to the present invention in the first position;

[0023] Figure 5 shows a schematic structural diagram of the crankshaft assembly in the pump body structure according to the present invention in the second position;

[0024] Figure 6 shows a schematic structural diagram of the crankshaft assembly in the pump body structure according to the present invention in the third position;

[0025] Figure 7 shows a schematic structural diagram of the crankshaft assembly in the pump body structure according to the present invention in the fourth position;

[0026] Figure 8 shows a top view of the assembly of the lower flange in the pump body structure according to the present invention;

[0027] Figure 9 shows a cross-sectional view of the lower flange in the pump body structure according to the present invention;

[0028] Figure 10 shows a schematic structural diagram of the first embodiment of the lower flange in the pump body structure according to the present invention;

[0029] Figure 11 The structural schematic diagram of the second embodiment of the lower flange in the pump body structure according to the present invention is shown.

[0030] Wherein, the above-mentioned drawings include the following reference numerals:

[0031] 100, crankshaft assembly; 200, lower flange; 300, flow guiding part; 210, through hole; 110, oil outlet hole; 301, first end; 302, second end; 310, first flow guiding section; 320, second flow guiding section; 321, first arc surface; 322, second arc surface; 220, fitting end face; 330, flow guiding groove; 331, main groove body; 332, sub-flow groove body; 400, sliding vane; 500, cylinder; 510, intake cavity; 520, exhaust cavity; 130, crankshaft body; 140, roller; 600, upper flange. Detailed implementation manners

[0032] It should be noted that, without conflict, the embodiments in the present application and the features in the embodiments may be combined with each other. The present invention will be described in detail below with reference to the drawings and in combination with the embodiments.

[0033] As mentioned in the background art, the existing compressors mainly include two parts, namely a pump body assembly and a motor, such as Figure 1As shown in the figure, the pump body assembly mainly includes a cylinder 500, a crankshaft body 130, a roller 140, a sliding vane 400, an upper flange 600 and a lower flange 200. The pump body crankshaft is in interference fit with the motor rotor. The R-shaped end face of the sliding vane contacts the outer circular surface of the roller in a line contact manner, and under the action of the spring force and the back pressure in the shell, the internal volume formed by the cylinder and the roller is divided into two crescent-shaped suction chambers and compression chambers. Inside the compressor pump body, the crankshaft and the roller are installed on the surface of the lower flange. Under the action of gravity, the lower thrust surface of the crankshaft and the lower end surface of the roller contact the end surface of the lower flange. During the operation of the compressor, the crankshaft rotates at a high speed and synchronously drives the roller to rotate. During this process, a relatively large area of relative movement occurs between the contact surfaces of the crankshaft, the roller and the lower flange. Moreover, as the frequency increases, this relative movement gradually becomes larger, which is the main part of the mechanical friction of the pump body. In addition, when the gas force and magnetic pull force existing during the operation of the compressor change, the movement forms of the crankshaft and the roller also change accordingly. They may move axially or tilt, resulting in a change in the contact form with the lower flange, thus aggravating the friction loss. At the same time, it will also affect the end face clearance. If the oil seal is insufficient, refrigerant leakage between high and low pressures will occur. It should be emphasized that when any one of the above three pump body parts is replaced with a ceramic material, due to the influence of the surface quality and hardness characteristics of the ceramic material, the wear will be further increased, which will have a greater impact on the operation energy efficiency and service life of the compressor. Therefore, in view of the above problems, the pump body structure provided in this application is provided with a diversion part 300 on the lower flange 200. The diversion part 300 is used to store lubricating fluid to lubricate the contact surface between the crankshaft assembly 100 and the lower flange 200 through the lubricating fluid. Among them, the diversion part 300 extends along a predetermined curve trajectory, and the extension direction is the same as the rotation direction of the crankshaft assembly 100. When the compressor is running, the lubricating fluid stored in the diversion part 300 is used for lubrication and sealing at any time. Since the extension direction of the diversion part 300 is the same as the rotation direction of the crankshaft assembly 100, when the crankshaft assembly 100 rotates to different angles, the diversion part 300 periodically covers the contact surface between the crankshaft assembly 100 and the lower flange 200. When the contact surface rotates past the upper end of the diversion part 300, the refrigerant oil in the groove is driven to flow into the end face clearance, ensuring that there is sufficient refrigerant oil between the end faces of the crankshaft assembly 100 and the lower flange 200 for lubrication, thereby reducing the friction loss and improving the lubrication conditions between the end faces, which is beneficial to the service life and operation energy efficiency of the compressor.

[0034] Please refer to Figures 2 to 11 , this application provides a pump body structure, including a crankshaft assembly 100 and a lower flange 200. The pump body structure further includes: a diversion part 300, which is arranged on the lower flange 200. The diversion part 300 is used to store lubricating fluid to lubricate the contact surface between the crankshaft assembly 100 and the lower flange 200 through the lubricating fluid. Among them, the diversion part 300 extends along a predetermined curve trajectory, and the extension direction is the same as the rotation direction of the crankshaft assembly 100.

[0035] According to the pump body structure of the present application, it includes a crankshaft assembly 100, a lower flange 200, and a diversion part 300. The diversion part 300 is arranged on the lower flange 200 and is used to store lubricating fluid, and lubricate the contact surface where the crankshaft assembly 100 contacts the lower flange 200 through the lubricating fluid. Among them, the diversion part 300 extends along a predetermined curve trajectory, and the extension direction is the same as the rotation direction of the crankshaft assembly 100. By setting it like this, when the crankshaft assembly 100 rotates and periodically contacts the lower flange 200, the lubricating fluid stored in the diversion part 300 can be used for lubrication, avoiding the problem that the friction force between the crankshaft assembly 100 and the lower flange 200 is too large, which in turn affects the service life of the pump body structure and the operating energy efficiency of the compressor.

[0036] Specifically, the design of the diversion part 300 enables the lubricating fluid to be effectively guided along the rotation direction of the crankshaft assembly 100 to the contact surface, ensuring the continuous supply of the lubricating fluid in this area, reducing the direct friction between the crankshaft assembly 100 and the lower flange 200, thereby reducing the frictional loss and improving the operating efficiency of the compressor. The presence of the lubricating fluid in the diversion part 300 not only plays a lubricating role but also can form a dynamic seal, effectively preventing the refrigerant leakage between the high-pressure chamber and the low-pressure chamber, ensuring the sealing performance of the compressor, and further improving the energy efficiency of the compressor. By providing continuous lubrication on the contact surface, the wear between parts is reduced. Especially when some components in the crankshaft assembly 100 adopt ceramic materials, the additional wear caused by the high hardness characteristics of the ceramic materials can be significantly reduced, thereby extending the service life and reliability of the pump body.

[0037] In a specific implementation, the lower flange 200 further includes a through-channel 210, at least part of the crankshaft assembly 100 is arranged in the through-channel 210, and the through-channel 210 is communicated with the oil outlet hole 110 of the crankshaft assembly 100; one end of the diversion part 300 is communicated with the through-channel 210, and the other end extends along the rotation direction of the crankshaft assembly 100. The lubricating oil in the oil outlet hole 110 flows through the through-channel 210 and then flows into the diversion part 300. By setting the through-channel 210 to be communicated with the oil outlet hole 110 of the crankshaft assembly 100, it can ensure that the lubricating oil directly and smoothly flows from the inside of the crankshaft body 130 to the contact friction surface. The design of the diversion part 300 further guides the lubricating oil to be accurately distributed along the rotation direction of the crankshaft to the contact area between the roller and the end face of the lower flange, thereby achieving an efficient lubrication effect and significantly reducing the frictional loss.

[0038] The diversion part 300 extends along the rotation direction of the crankshaft assembly 100, and can form a dynamic sealing interface, effectively preventing the leakage of high-pressure refrigerant. Especially during the operation of the compressor, when different pressures and magnetic pulling forces act on the system, the diversion part 300 can provide instantaneous sealing enhancement according to the movement characteristics of the crankshaft and the roller, preventing the refrigerant from leaking between the high-pressure and low-pressure chambers, and improving the operating efficiency of the compressor. For compressors using ceramic materials (such as rollers), the combined design of the through-channel 210 and the diversion part 300 can more effectively address the additional wear problems caused by the hardness and surface characteristics of ceramic parts. By increasing the supply of lubricating oil and improving its distribution, the impact of these material changes on the performance of the compressor is mitigated.

[0039] By using the oil outlet hole 110 on the crankshaft body 130 to supply oil to the diversion part 300, when the compressor is running, the crankshaft body 130 rotates at a high speed. Under the action of centrifugal force, the refrigerating oil at the bottom of the housing is pumped upward through the center of the crankshaft. Part of the refrigerating oil will flow out from the oil outlet hole 110 of the short shaft of the crankshaft during the pumping process and gather in the gap between the through-channel 210 of the lower flange 200 and the crankshaft body 130. When the oil level in the gap rises to a certain height, the refrigerating oil will flow into the diversion part 300 along the inlet of the diversion part 300 connected to the gap and be stored in the diversion part 300 for lubrication and sealing at any time.

[0040] In this application, the pump body structure further includes a sliding vane 400. The diversion part 300 includes a relatively arranged first end 301 and a second end 302. The first end 301 is communicated with the through-channel 210; the included angle between the plane where the center line of the first end 301 is located and the sliding vane 400 is θ1, and θ1 > 200°; the included angle between the plane where the end face of the second end 302 is located and the sliding vane 400 is θ2, and θ2 ≤ 330°. Among them, the included angles θ1 and θ2 are respectively the included angles between the first end 301 and the second end 302 and the center line of the sliding vane 400. Since the included angle θ1 between the first end 301 and the sliding vane 400 is > 200°, when the crankshaft drives the roller to rotate, the lubricating oil can cover the friction surface for a longer time, providing continuous lubrication and significantly reducing the friction loss. The included angle θ2 between the plane where the end face of the second end 302 is located and the sliding vane 400 is controlled below 330°. This design effectively avoids the disorderly flow of the lubricating oil between the high-pressure area and the low-pressure area, reduces the leakage of the lubricating oil caused by the pressure gradient. At the same time, due to the setting of the diversion part 300, a sealing barrier is formed between its end face and the sliding vane 400, further preventing the leakage of high-pressure refrigerant to the low-pressure side and improving the airtightness and energy efficiency of the compressor.

[0041] In the specific implementation process, the diversion part 300 includes a first diversion section 310 and a second diversion section 320 that are interconnected. The first diversion section 310 is connected to the threading channel 210 and extends along a first arc-shaped trajectory, while the second diversion section 320 extends along a second arc-shaped trajectory. Since the first diversion section 310 is connected to the threading channel 210 and extends along the first arc-shaped trajectory, the flow path of the lubricating oil inside the pump body is optimized. After entering from the threading channel 210, the lubricating oil naturally flows along the first arc-shaped trajectory to the second diversion section 320, and then is more precisely guided to the contact area between the roller, the crankshaft and the lower flange end face, improving the targeting and efficiency of lubrication.

[0042] The second diversion section 320 extends along the second arc-shaped trajectory. This design helps to form a stable oil film during the operation of the compressor, enhancing the sealing effect between the contact surfaces, effectively preventing the leakage of high-pressure refrigerant from the compression chamber to the low-pressure suction chamber, and improving the working efficiency and reliability of the compressor.

[0043] Through the dual oil diversion mechanism of the first diversion section 310 and the second diversion section 320, it is ensured that the contact surfaces are always in a fully lubricated state, which can significantly reduce the friction between the crankshaft, the roller and the lower flange end face, reduce the probability of wear, and extend the service life of the compressor. The arc-shaped trajectory design of the first diversion section 310 and the second diversion section 320 avoids the stress concentration problem that may be caused by straight grooves, improves the structural stability and strength of the lower flange, and reduces the potential risks of material fatigue and deformation.

[0044] Among them, the second diversion section 320 includes a first arc-shaped surface 321 and a second arc-shaped surface 322 that are opposite and spaced apart. A diversion space for guiding the lubricating oil is provided between the first arc-shaped surface 321 and the second arc-shaped surface 322. The first arc-shaped surface 321 is arranged closer to the threading channel 210 than the second arc-shaped surface 322. The crankshaft assembly 100 includes a thrust surface that fits with the lower flange 200; the radius of the circle where the thrust surface is located is R1, the inner radius of the threading channel 210 is R4, the radius of the circle where the second arc-shaped surface 322 is located is R2, and the radius of the circle where the first arc-shaped surface 321 is located is R3; where, R1 - R2 ≥ 2mm; R3 - R4 ≥ 2mm. Through the diversion space between the first arc-shaped surface 321 and the second arc-shaped surface 322, the lubricating oil can be precisely guided to the contact area between the thrust surface and the lower flange 200, ensuring the effective utilization of the lubricating liquid and avoiding the waste of oil liquid and other side effects that may be caused by over-lubrication.

[0045] The first arc surface 321 is closer to the through-channel 210, while the second arc surface 322 is farther away from the channel. This design enables the establishment of a continuous lubricating film in the gap where the crankshaft assembly 100 contacts the lower flange 200, effectively isolating the high and low pressure chambers, enhancing the overall sealing performance, reducing refrigerant leakage, and being conducive to improving the operating efficiency of the compressor. The design parameters of the first arc surface 321 and the second arc surface 322 (such as R1, R2, R3, R4 and the distances between them) are strictly calculated to ensure that the diversion part 300 can maintain good structural stability and strength while withstanding various loads during the operation of the compressor. The specific dimensional relationships R1 - R2 ≥ 2 mm and R3 - R4 ≥ 2 mm ensure sufficient clearance for the lubricating oil to flow, and also prevent structural interference caused by too small a clearance.

[0046] The lower flange 200 includes a fitting end face 220 that fits with the crankshaft assembly 100. At least part of the diversion part 300 is arranged on the fitting end face 220. The diversion part 300 includes: a diversion groove 330, and the extending direction of the diversion groove 330 is the same as the rotation direction of the crankshaft assembly 100. The diversion groove 330 is designed along the rotation direction of the crankshaft assembly 100, ensuring that the lubricating fluid can be accurately and continuously guided to the contact area between the crankshaft assembly 100 and the lower flange 200, improving the accuracy of lubrication and reducing the waste of lubricating fluid. Through the diversion groove 330 on the fitting end face 220, a dynamic sealing film is formed on the contact surface, which can effectively isolate the high-pressure chamber and the low-pressure chamber, prevent refrigerant leakage during operation, and improve the sealing performance and energy efficiency of the compressor. When the oil level in the gap between the crankshaft body 130 and the through-channel 210 rises to a certain height, the oil flows into the interior of the diversion groove along the inlet where the diversion groove 330 communicates with the gap and is stored in the diversion groove 330 for lubrication and sealing at any time.

[0047] Among them, the first end opening of the diversion groove 330 communicates with the through-channel 210, and the included angle between the plane where the center line of the first end opening is located and the center line of the sliding vane 400 is θ1, and θ1 > 200°; the included angle between the end face of the second end of the diversion groove 330 and the center line of the sliding vane 400 is θ2, and θ2 ≤ 330°.

[0048] Specifically, in the embodiment provided in the present application, the width of the diversion groove 330 is T, and the depth is H, where 1 mm ≤ T ≤ 3 mm and H ≤ 2.5 mm.

[0049] Since the amount of refrigerant oil pumped upward through the central oil hole of the crankshaft body 130 and flowing out from the oil hole on the short shaft side is uncontrollable, the oil level in the inner circular sunk groove of the lower flange (i.e., the part with a gap between the through-channel 210 and the crankshaft body 130, which is the inner circular sunk groove of the lower flange) can be high or low. If the volume of the diversion groove 330 is designed too large, the oil level inside the diversion groove 330 will be too low to contact the end face, and the ideal lubrication and sealing effect cannot be achieved. Therefore, the volume design of the diversion groove 330 will affect the actual oil storage, lubrication and sealing effect. In order to lubricate and seal the end face in the largest range, the bending length of the diversion groove 330 should be as wide as possible. Therefore, its cross-sectional area should not be too large. Combining the experimental verification conclusions of this structure, if the width of the diversion groove 330 is T and the sinking depth is H, it is necessary to satisfy: 1mm ≤ T ≤ 3mm, H ≤ 2.5mm.

[0050] In another embodiment provided by the present application, as Figure 11 shown, a through-channel 210 for the crankshaft assembly 100 to pass through is provided on the lower flange 200. The diversion groove 330 includes: a main groove body 331, one end of the main groove body 331 is communicated with the through-channel 210, and the other end extends along the rotation direction of the crankshaft assembly 100; a diversion groove body 332, which is communicated with the main groove body 331. There are multiple diversion groove bodies 332, and the multiple diversion groove bodies 332 are arranged at intervals along the extension direction of the main groove body 331. The difference between this embodiment and the above embodiment is that multiple diversion groove bodies 332 are provided, which can effectively disperse the pressure of the lubricating oil, avoiding problems such as oil overflow or uneven pressure that may occur in a single groove body during high-speed rotation. Through the dispersion effect of the diversion groove body 332, the lubricating oil can cover the contact surface more evenly, improving the lubrication conditions. The combined design of the main groove body 331 and the diversion groove body 332 not only enhances the supply of lubricating oil, but also forms a complex oil film sealing path, effectively preventing the leakage of high-pressure gas to the low-pressure area during the operation of the compressor. This multi-stage sealing structure significantly improves the sealing performance of the compressor and reduces energy loss.

[0051] The width of the main groove body 331 is T, and the width of the diversion groove body 332 is T1, where T1 = 0.5 - 0.8T. The width ratio of the main groove body 331 and the diversion groove body 332 (T1 = 0.5 - 0.8T) ensures that the structural strength of the lower flange 200 is not affected while providing sufficient lubricating oil storage space. The reasonable size design avoids weakening the bearing capacity of the lower flange due to the too-wide groove body and prevents insufficient lubrication caused by the too-narrow groove body.

[0052] In this embodiment, each diversion groove body 332 extends along a predetermined arc-shaped trajectory, so that when contacting the crankshaft body 130 and the roller 140, the lubricating oil can form multiple oil films on the contact surface, effectively isolating the high-pressure gas and the low-pressure gas, significantly improving the sealing performance of the compressor, and at the same time, each diversion groove body 332 can be used to store the oil.

[0053] The pump body structure further includes: a cylinder 500 sleeved on the crankshaft assembly 100. The cylinder 500 includes an intake chamber 510 and an exhaust chamber 520, and the flow guiding portion 300 is disposed opposite to the exhaust chamber 520. Since there are high and low pressure chambers inside the cylinder, in order to prevent the refrigerating oil in the oil guiding groove from leaking into the low pressure chamber of the cylinder under the action of pressure, the oil guiding groove should be arranged on the high pressure side of the cylinder exhaust chamber.

[0054] The present application also provides a compressor, including a body and a pump body structure. The pump body structure is disposed inside the body, and the pump body structure is the pump body structure of the above embodiment.

[0055] In the lower flange structure of the rotary compressor provided by the present application, an oil guiding groove 330 is opened on the fitting end face 220 of the lower flange 200 to achieve the purpose of guiding and storing oil. This design is mainly aimed at effectively improving the friction loss and leakage problems between the lower thrust surface of the crankshaft and the lower end surface of the roller 140 and the end face of the lower flange 200 during the operation of the rotary compressor, especially when some of the above parts are replaced with ceramic materials (such as the roller), the friction loss is further aggravated.

[0056] Specifically, at least one of the crankshaft body 130, the roller 140, and the lower flange 200 is made of a ceramic material, including but not limited to zirconia, alumina, silicon carbide, etc. An oil guiding groove 330 is opened on the fitting end face 220 of the lower flange 200. The starting point of the oil guiding groove 330 is connected to the inner circular sink of the lower flange 200, and its extending direction needs to be the same as the rotating direction of the crankshaft body 130 and the roller 140, and bends clockwise or counterclockwise. Among them, there are multiple oil guiding grooves 330, and the number of them is set as n. Depending on the design range of the parts, n≥1 can be selected. This structure can improve the friction loss and leakage problems between the lower thrust surface of the crankshaft and the lower end surface of the roller and the large end face of the lower flange during the operation of the compressor, and ensure the operation energy efficiency of the compressor.

[0057] The present invention proposes to open an oil guiding groove on the end face of the lower flange. This oil guiding groove is connected to the inner circular sink of the lower flange. When the compressor operates, the crankshaft rotates at a high speed. Under the action of centrifugal force, the refrigerating oil at the bottom of the housing is pumped upward through the hollow in the center of the crankshaft. Part of the refrigerating oil will flow out from the side oil hole of the short shaft of the crankshaft and gather at the inner circular sink of the lower flange during the pumping process. When the oil level in the sink rises to a certain height, the refrigerating oil will flow into the oil guiding groove through the inlet connected to the inner circular sink of the lower flange and be stored in the groove for lubrication and sealing at any time.

[0058] Such as Figures 4 to 7As shown in the figure, when the crankshaft roller rotates to different angles, the oil guiding groove periodically covers the lower thrust surface of the crankshaft and the lower end surface of the roller. When the end surface rotates past the upper end of the oil guiding groove, it drives the refrigerating oil in the groove to flow into the end surface gap, ensuring that there is sufficient refrigerating oil between the crankshaft roller and the lower flange end surface for lubrication, thereby reducing frictional losses and improving the lubrication conditions between the end surfaces, and preventing the leakage of high and low pressure refrigerants.

[0059] As Figure 8 shown in the top view of the assembly of the lower flange of the crankshaft in the optimal embodiment of the present invention. If the oil guiding groove is designed as a radial straight line, its limit lubrication length is limited by the outer diameter of the roller and the sealing safety distance and cannot reach the optimal upper limit. Preferably, as shown in the attached drawing, the extension direction of the oil guiding groove from the inner circle to the outer circle should be the same as the rotation direction of the crankshaft and the roller, and bend clockwise or counterclockwise, so as to broaden the maximum design range of the oil guiding groove to achieve the optimal lubrication and sealing effects, and set the number of its openings as n, and n≥1 can be selected according to the design range of the parts.

[0060] At the same time, since there are high and low pressure chambers inside the cylinder, in order to prevent the refrigerating oil in the oil guiding groove from leaking into the low pressure chamber of the cylinder under the action of pressure, the oil guiding groove should be arranged on the high pressure side of the cylinder exhaust. Preferably, according to the empirical values of the starting and ending angles of the exhaust of most rotary compressors, let the starting angle of the bend of the oil guiding groove be θ1 and the ending angle of the bend be θ2, and it is necessary to ensure that: θ1>200°, θ2≤330°.

[0061] In addition, if the bending curvature of the oil guiding groove is too large, it will cause the oil guiding groove to extend into the sink between the lower thrust surface and the eccentric circle of the crankshaft. Under the action of pressure, part of the refrigerating oil in the oil guiding groove may flow into this crankshaft sink, resulting in a reduction in the amount of oil in the oil guiding groove, which is not conducive to providing lubrication and sealing for the end surface; if the bending curvature is too small, the wall thickness of the side wall of the oil guiding groove close to the inner circle of the lower flange is insufficient, affecting the structural strength. Therefore, let the outer radius of the lower thrust surface of the crankshaft be R1, the outer radius of the oil guiding groove be R2, the inner radius be R3, and the inner radius of the lower flange be R4, and it is necessary to satisfy: R1 - R2≥2mm, R3 - R4≥2mm.

[0062] As Figure 9 and Figure 10 shown in the figure, since the amount of refrigerating oil pumped upward through the central oil hole of the crankshaft and flowing out from the oil hole on the short shaft side is uncontrollable, the oil level in the inner circle sink of the lower flange can be high or low. If the volume of the oil guiding groove is designed too large, it will cause the oil level inside the groove to be too low to contact the end surface, and the ideal lubrication and sealing effects cannot be achieved. Therefore, the volume design of the oil guiding groove will affect the actual oil storage, lubrication and sealing effects. In order to lubricate and seal the end surface in the largest range, the bending length of the groove should be as wide as possible, so its cross-sectional area should not be too large. Combining the experimental verification conclusions of this structure, let the width of the oil guiding groove be T and the sinking depth be H, and it is necessary to satisfy: 1mm≤T≤3mm, H≤2.5mm.

[0063] The pump body structure of the present application is applicable not only to rotary compressors, but also to rotary fluid machines with similar structures, such as rotary expanders, sliding vane compressors, sliding vane expanders, etc.

[0064] From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:

[0065] According to the pump body structure of the present application, it includes a crankshaft assembly 100, a lower flange 200 and a diversion part 300. The diversion part 300 is arranged on the lower flange 200 and is used to store lubricating fluid, and the contact surface where the crankshaft assembly 100 contacts the lower flange 200 is lubricated by the lubricating fluid. Among them, the diversion part 300 extends along a predetermined curve trajectory, and the extending direction is the same as the rotation direction of the crankshaft assembly 100. With such a setting, when the crankshaft assembly 100 periodically contacts the lower flange 200 during rotation, the lubricating fluid stored in the diversion part 300 can be used for lubrication, avoiding the problem that the frictional force between the crankshaft assembly 100 and the lower flange 200 is too large, thereby affecting the service life of the pump body structure and the operation energy efficiency of the compressor.

[0066] The above are only the preferred embodiments of the present invention and are not used to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A pump body structure, comprising a crankshaft assembly (100) and a lower flange (200), characterized in that, The pump body structure further includes: A diversion part (300) is arranged on the lower flange (200). Lubricating fluid is stored in the diversion part (300) to lubricate the contact surface where the crankshaft assembly (100) contacts the lower flange (200) through the lubricating fluid. Wherein, the diversion part (300) extends along a predetermined curve trajectory, and the extension direction is the same as the rotation direction of the crankshaft assembly (100).

2. The pump body structure according to claim 1, wherein, The lower flange (200) further includes a through-channel (210). At least part of the crankshaft assembly (100) is arranged in the through-channel (210), and the through-channel (210) is communicated with the oil outlet hole (110) of the crankshaft assembly (100). One end of the diversion part (300) is communicated with the through-channel (210), and the other end extends along the rotation direction of the crankshaft assembly (100). The lubricating oil in the oil outlet hole (110) flows into the diversion part (300) after flowing through the through-channel (210).

3. The pump body structure according to claim 2, characterized in that, The pump body structure further includes a sliding vane (400). The diversion part (300) includes a first end (301) and a second end (302) arranged opposite to each other. The first end (301) is communicated with the through-channel (210). The included angle between the plane where the center line of the first end (301) is located and the sliding vane (400) is θ1, and θ1 > 200°. The included angle between the plane where the end face of the second end (302) is located and the sliding vane (400) is θ2, and θ2 ≤ 330°.

4. The pump body structure according to claim 2, wherein, The diversion part (300) includes: A first diversion section (310) and a second diversion section (320) which are communicated with each other. The first diversion section (310) is communicated with the through-channel (210). The first diversion section (310) extends along a first arc trajectory, and the second diversion section (320) extends along a second arc trajectory.

5. The pump body structure according to claim 4, characterized in that, The second diversion section (320) includes a first arc surface (321) and a second arc surface (322) which are opposite and spaced apart. A diversion space for diverting the lubricating oil is arranged between the first arc surface (321) and the second arc surface (322). The first arc surface (321) is arranged closer to the through-channel (210) than the second arc surface (322). The crankshaft assembly (100) includes a thrust surface that fits with the lower flange (200). The radius of the circle where the thrust surface is located is R1, the inner radius of the through-channel (210) is R4, the radius of the circle where the second arc surface (322) is located is R2, and the radius of the circle where the first arc surface (321) is located is R3. Wherein, R1 - R2 ≥ 2 mm; R3 - R4 ≥ 2 mm.

6. The pump body structure according to claim 1, characterized in that, The lower flange (200) includes a fitting end face (220) that fits with the crankshaft assembly (100). At least part of the diversion part (300) is arranged on the fitting end face (220). The diversion part (300) includes: The diversion channel (330), and the extending direction of the diversion channel (330) is the same as the rotation direction of the crankshaft assembly (100).

7. The pump body structure according to claim 6, characterized in that, The width of the diversion channel (330) is T, and the depth is H, where 1 mm ≤ T ≤ 3 mm, and H ≤ 2.5 mm.

8. The pump body structure according to claim 6, wherein A through-channel (210) for the crankshaft assembly (100) to pass through is provided on the lower flange (200), and the diversion channel (330) includes:[[]] A main channel body (331), one end of the main channel body (331) is communicated with the through-channel (210), and the other end extends along the rotation direction of the crankshaft assembly (100); Diversion channel bodies (332), which are communicated with the main channel body (331), there are a plurality of the diversion channel bodies (332), and the plurality of diversion channel bodies (332) are arranged at intervals along the extending direction of the main channel body (331).

9. The pump body structure according to claim 8, characterized in that, The width of the main channel body (331) is T, and the width of the diversion channel body (332) is T1, where T1 = (0.5 - 0.8)T.

10. The pump body structure according to claim 1, characterized in that, The pump body structure further includes:[[]] A cylinder (500), sleeved on the crankshaft assembly (100), the cylinder (500) includes an intake cavity (510) and an exhaust cavity (520), and the diversion part (300) is oppositely arranged to the exhaust cavity (520).

11. A compressor, comprising a body and a pump body structure, the pump body structure being disposed within the body, characterized in that, The pump body structure is the pump body structure according to any one of claims 1 to 10.

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