Double-cone oil cavity structure of high-rotating-speed diaphragm compressor and manufacturing method thereof

Abstract

The invention discloses a double-cone oil cavity structure of a high-rotating-speed diaphragm compressor and a manufacturing method of the double-cone oil cavity structure. The double-cone oil cavity structure of the high-rotating-speed diaphragm compressor comprises a cylinder cover and a supporting assembly. The cylinder cover is installed on the supporting assembly, a diaphragm and an oil distribution disc are arranged between the supporting assembly and the cylinder cover, a first oil cavity is formed between the supporting assembly and the bottom of the oil distribution disc, the oil distribution disc is provided with an oil outlet channel, the bottom of the oil distribution disc is provided with a first conical protruding part, a piston hole is formed in the supporting assembly, and a piston is arranged in the piston hole. The top of the piston is in a second cone shape, and the first cone shape and the second cone shape are oppositely arranged. The top of the piston is in the second cone shape, and the first cone-shaped protruding part is arranged at the bottom of the oil distribution disc, so that when the piston moves from a lower dead center to an upper dead center, hydraulic oil can be guided to flow in the first oil cavity in the radial direction, impact of the hydraulic oil on the oil distribution disc is reduced, and the flowing loss of the hydraulic oil is reduced; therefore, the cavitation phenomenon is prevented.

Description

Technical Field

[0001] The invention relates to the field of diaphragm compressors, and in particular to a double-cone oil cavity structure of a high-speed diaphragm compressor and a manufacturing method thereof. Background Art

[0002] Cavitation of hydraulic oil under high-speed flow is an important factor affecting the high-speed of diaphragm compressors. Cavitation refers to the process of the appearance, formation, development and collapse of cavities (cavities) containing liquid vapor or air inside the liquid flow field or on the liquid-solid interface.

[0003] In the existing diaphragm compressor oil chamber, when the hydraulic oil flow cross-section changes, the local area pressure of the hydraulic oil drops rapidly, causing air to precipitate in the oil and produce cavitation. The cavitation then ruptures in the high-pressure area. The high temperature, high pressure and high-speed impact generated by the rupture will cause cavitation damage to the diaphragm head material and generate hydraulic noise.

[0004] Based on this, there is an urgent need for a high-speed diaphragm compressor double-cone oil chamber structure to prevent cavitation. Summary of the invention

[0005] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a double-cone oil chamber structure of a high-speed diaphragm compressor and a manufacturing method thereof.

[0006] According to the first aspect of the present invention, a double-cone oil chamber structure of a high-speed diaphragm compressor includes a cylinder head and a support assembly; the cylinder head is installed on the support assembly, and a diaphragm and an oil distribution plate arranged in sequence in the up and down directions are provided between the support assembly and the cylinder head, a first oil chamber is provided between the support assembly and the bottom of the oil distribution plate, the oil distribution plate has an oil outlet channel, a second oil chamber is provided between the top of the oil distribution plate and the diaphragm, the bottom of the oil distribution plate has a protrusion extending into the first oil chamber, the protrusion is in a first cone shape, the support assembly has a piston hole connected to the first oil chamber, a piston that can move up and down is provided in the piston hole, the top of the piston is in a second cone shape, and the first cone and the second cone are arranged opposite to each other.

[0007] The double-conical oil chamber structure of the high-speed diaphragm compressor according to the embodiment of the present invention has at least the following technical effects: by making the top of the piston into a second cone and providing a protrusion in the shape of a first cone at a position corresponding to the piston hole at the bottom of the oil distribution plate, when the piston moves from the lower dead center to the upper dead center, the hydraulic oil can be guided to flow radially in the first oil chamber, thereby reducing the impact of the hydraulic oil on the oil distribution plate and reducing the flow loss of the hydraulic oil, thereby preventing the occurrence of cavitation and providing stability in the operation of the high-speed diaphragm compressor.

[0008] According to some embodiments of the present invention, the support assembly includes a cylinder body, the cylinder head and the oil distribution plate are both installed on the cylinder body, the bottom of the oil distribution plate has a first concave cavity, the longitudinal section of the first concave cavity includes two first inclined side walls, the protrusion is located between the two first inclined side walls, the top of the cylinder body has a second concave cavity connected to the piston hole, the longitudinal section of the second concave cavity includes two second inclined side walls and a bottom wall located between the two second inclined side walls, the first inclined side wall, the protrusion, the second inclined side wall and the bottom wall enclose the first oil cavity.

[0009] According to some embodiments of the present invention, the second inclined side wall includes an inclined section and a rounded section, two ends of the inclined section are respectively connected to the rounded section and the bottom wall, and the top of the piston hole has a rounded portion.

[0010] According to some embodiments of the present invention, the height of the first oil chamber is defined as h. The height h of the first oil chamber first gradually increases and then gradually decreases along the increase of a diameter d. The diameter d gradually increases along the radial direction of the first oil chamber. The piecewise function expression 1 is:

[0011]

[0012] Among them, H is the distance between the bottom wall and the end of the second inclined side wall away from the bottom wall, α1 is the cone angle of the first cone, α2 is the angle between the two first inclined side walls, α3 is the angle between the two inclined sections, D1 is the diameter of the first inclined side wall at the end away from the protrusion, D2 is the diameter of the bottom of the first cone, D3 is the diameter of the connection between the second inclined side wall and the bottom wall, and D4 is the diameter of the connection between the inclined section and the chamfered section.

[0013] According to some embodiments of the present invention, a central axis of the oil outlet channel is perpendicular to the first inclined side wall.

[0014] According to some embodiments of the present invention, the oil distribution plate includes an oil distribution part and a supporting part, the oil distribution part is located inside the supporting part, the oil outlet channel, the first concave cavity and the protrusion are all located on the oil distribution part, the supporting part rests on the cylinder body, and the diameter D7 of the oil distribution part is 1 / 3 to 2 / 3 times the diameter D6 of the oil distribution plate.

[0015] According to some embodiments of the present invention, the oil distribution plate is formed with a plurality of circles of oil outlet groups spaced apart along the radial direction of the oil distribution plate, each circle of the oil outlet group includes a plurality of oil outlet channels spaced apart along the circumferential direction of the oil distribution plate, and on a horizontal projection plane, the oil outlet group located in the innermost circle is located outside the piston, the sum of the flow areas of the plurality of oil outlet channels is S1, the area of ​​the piston hole is S2, and S1 is 1.5 to 2.5 times that of S2.

[0016] According to some embodiments of the present invention, the top of the oil distribution plate has an oil guide groove for guiding the hydraulic oil to the edge of the second oil chamber.

[0017] According to some embodiments of the present invention, an oil overflow hole and an oil replenishing hole are provided at the edge of the oil distribution plate corresponding to the second oil chamber, and the support assembly has an oil overflow channel and an oil replenishing channel, the oil overflow hole is connected to the oil overflow channel, and the oil replenishing hole is connected to the oil replenishing channel.

[0018] A method for manufacturing a high-speed diaphragm compressor double-cone oil chamber structure according to a second embodiment of the present invention is used to obtain the high-speed diaphragm compressor double-cone oil chamber structure according to the first embodiment, comprising the following steps:

[0019] Step 1: Determine the diameter D5 of the piston, the cone angle α4 of the second cone, and the cone angle α1 of the first cone, α4 is 160° to 180°, α1 is 140° to 160°, and the diameter D2 of the bottom of the first cone is equal to the diameter D5 of the piston; D5 is obtained by expression 2, which is:

[0020]

[0021] Wherein, Q is the exhaust volume of the diaphragm compressor (m3 / s), n is the rotation speed of the crankshaft of the diaphragm compressor (rpm), and L is the stroke of the piston (500) (m);

[0022] Step 2: Determine the D1 and the α2, α2 = 168° to 176°, the diameter D6 of the oil distribution plate (400) is greater than or equal to 2 times D1; ​​D1 is obtained by expression 3, which is:

[0023]

[0024] Where, Q is the exhaust volume of the diaphragm compressor (m3 / s), n is the speed of the crankshaft of the diaphragm compressor (rpm), and W 0 is the maximum deflection (mm) of the diaphragm (300), and z is the deflection index of the diaphragm (300);

[0025] Step 3: Determine the α3, D4 and D3, α3 is 164° to 172°, D4 is 5 mm to 10 mm smaller than D1, and D3 is 240 mm;

[0026] Step 4: Arrange a plurality of oil outlet channels on the oil distribution plate.

[0027] The manufacturing method of the double-cone oil chamber structure of a high-speed diaphragm compressor according to the second embodiment of the present invention has at least the following technical effects: the double-cone oil chamber structure of a high-speed diaphragm compressor is designed by the above method to prevent the occurrence of cavitation and provide stability in the operation of the high-speed diaphragm compressor.

[0028] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0030] Figure 1 A cross-sectional view of a double-cone oil chamber structure of a high-speed diaphragm compressor according to an embodiment of the present invention;

[0031] Figure 2 This is an exploded view of the double-cone oil chamber structure of a high-speed diaphragm compressor;

[0032] Figure 3 for Figure 1 The enlarged view of point A in the middle;

[0033] Figure 4 Also for Figure 1 The enlarged view of point A in the middle;

[0034] Figure 5 This is a bottom view of the oil distribution plate;

[0035] Figure 6 This is a schematic diagram of the bottom structure of the oil distribution plate;

[0036] Figure 7 It is a schematic diagram of the top structure of the oil distribution plate;

[0037] Figure 8 This is the front view of the piston.

[0038] Reference numerals: cylinder head 100, support assembly 200, first oil chamber 210, piston hole 220, rounded corner portion 221, cylinder body 230, second concave cavity 231, second inclined side wall 2311, bottom wall 2312, inclined section 2313, rounded corner section 2314, oil overflow channel 232, oil replenishment channel 233, cylinder sleeve 240, cylinder seat 250, diaphragm 300, oil distribution plate 400, oil overflow hole 4 01, oil replenishing hole 402, annular air inlet groove 403, oil outlet channel 410, flow groove 411, flow hole 412, protrusion 420, first cone 421, first concave cavity 430, first inclined side wall 431, oil distribution part 440, support part 450, annular oil outlet channel group 460, second oil cavity 470, edge 471, oil inlet groove 480, piston 500, second cone 510. DETAILED DESCRIPTION

[0039] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0040] In the description of the present invention, it should be understood that descriptions involving orientations, such as up, down, front, back, left, right, etc., and orientations or positional relationships indicated are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0041] In the description of the present invention, the meaning of "above", "below", "exceed", etc. is not inclusive of the number itself, and the meaning of "above", "below", "within", etc. is inclusive of the number itself. If there is a description of "first" or "second", it is only used to distinguish the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0042] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0043] Reference Figure 1 , 2As shown, the double-cone oil chamber structure of the high-speed diaphragm compressor according to the first embodiment of the present invention includes a cylinder head 100 and a support assembly 200; the cylinder head 100 is mounted on the support assembly 200, and a diaphragm 300 and an oil distribution plate 400 are arranged in sequence along the up-down direction between the support assembly 200 and the cylinder head 100, as shown in FIG. Figure 3 As shown, a first oil chamber 210 is provided between the support assembly 200 and the bottom of the oil distribution plate 400, the oil distribution plate 400 has an oil outlet channel 410, a second oil chamber 470 is provided between the top of the oil distribution plate 400 and the diaphragm 300, the bottom of the oil distribution plate 400 has a protrusion 420 extending into the first oil chamber 210, the protrusion 420 is in a first cone shape 421, the support assembly 200 has a piston hole 220 connected to the first oil chamber 210, a piston 500 that can move up and down is provided in the piston hole 220, the top of the piston 500 is in a second cone shape 510, and the first cone 421 and the second cone 510 are arranged opposite to each other.

[0044] According to the calculation formula of local resistance loss, when the hydraulic oil density and local loss coefficient are constant, the greater the flow rate of the hydraulic oil, the greater the local loss. Therefore, in high-speed diaphragm compressors, reducing the flow rate of the hydraulic oil and reducing the sudden change of the flow cross section, thereby reducing the local resistance loss of the hydraulic oil, will effectively prevent the occurrence of cavitation and is beneficial to the stability of the operation of the diaphragm compressor.

[0045] Furthermore, the present invention makes the top of the piston 500 have a second cone 510 and provides a protrusion 420 with a first cone 421 at a position corresponding to the piston hole 220 at the bottom of the oil distribution plate 400, so that when the piston 500 moves from the lower dead center to the upper dead center, the hydraulic oil can be guided to flow in the first oil chamber 210 along the radial direction (left and right direction), thereby reducing the impact of the hydraulic oil on the oil distribution plate 400 and reducing the flow loss of the hydraulic oil, thereby preventing the occurrence of cavitation and providing stability in the operation of the high-speed diaphragm compressor.

[0046] Specifically, both the first cone 421 and the second cone 510 may be in a cone shape, or only the first cone 421 may be in a cone shape, and the second cone 510 may be in a truncated cone shape.

[0047] In some embodiments of the present invention, Figure 1 , 3As shown, the support assembly 200 includes a cylinder body 230, and the cylinder head 100 and the oil distribution plate 400 are both installed on the cylinder body 230. The bottom of the oil distribution plate 400 has a first concave cavity 430, and the longitudinal section of the first concave cavity 430 includes two first inclined side walls 431, and the protrusion 420 is located between the two first inclined side walls 431. The top of the cylinder body 230 has a second concave cavity 231 connected to the piston hole 220, and the longitudinal section of the second concave cavity 231 includes two second inclined side walls 2311 and a bottom wall 2312 located between the two second inclined side walls 2311. The first inclined side walls 431, the protrusion 420, the second inclined side walls 2311 and the bottom wall 2312 enclose a first oil chamber 210.

[0048] like Figure 4 As shown, since the first oil chamber 210 is formed by the first concave cavity 430, the protrusion 420 and the second concave cavity 231, the upper and lower walls on the left and right sides of the first oil chamber 210 respectively form a "<" shape and a ">" shape, so that the height h of the first oil chamber 210 gradually decreases along the radial direction, so that the flow dead zone of the hydraulic oil is reduced, the volume of the first oil chamber 210 is reduced, and thus the filling amount of the hydraulic oil is reduced, and the influence of the volumetric efficiency caused by the compressibility of the hydraulic oil under high speed conditions is reduced.

[0049] Specifically, Figure 3 As shown, the size of the first cavity 430 in the radial direction (left-right direction) is equal to the size of the second cavity 231 in the radial direction (left-right direction) and both are larger than the size of the piston hole 220 in the radial direction.

[0050] Specifically, Figure 1 As shown, the support assembly 200 also includes a cylinder sleeve 240 and a cylinder seat 250. The cylinder seat 250 is fixed to the bottom of the cylinder body 230 by screws. The cylinder sleeve 240 is inserted into the cylinder sleeve 240 and the cylinder body 230 and fixed to the cylinder seat 250 by screws. The piston hole 220 is set on the cylinder sleeve 240.

[0051] Specifically, Figure 2 As shown, the cross-sections of the cylinder head 100, the diaphragm 300, the oil distribution plate 400, the cylinder block 230, the cylinder sleeve 240, the cylinder base 250 and the piston 500 are all circular.

[0052] Specifically, Figure 3 As shown, the protrusion 420 is located at the center of the bottom of the oil distribution plate 400 , and the piston 500 is located directly below the protrusion 420 .

[0053] Specifically, Figure 1As shown, in order to prevent leakage of hydraulic oil, a first seal is arranged between the piston 500 and the piston hole 220, and the first seal includes multiple sealing rings; a second seal is arranged between the cylinder sleeve 240 and the cylinder seat 250, and the second seal includes multiple sealing rings; the top of the cylinder body 230 has a groove, the oil distribution plate 400 is installed in the groove, and a third seal is arranged between the bottom surface of the oil distribution plate 400 and the bottom surface of the groove; a fourth seal is arranged between the diaphragm 300 and the oil distribution plate 400.

[0054] In a further embodiment of the present invention, Figure 3 As shown, the second inclined side wall 2311 includes an inclined section 2313 and a rounded section 2314, and the two ends of the inclined section 2313 are respectively connected to the rounded section 2314 and the bottom wall 2312, and the top of the piston hole 220 has a rounded portion 221. By providing the rounded section 2314 at the top of the side of the second concave cavity 231 and providing the rounded portion 221 at the connection between the piston hole 220 and the first oil chamber 210, the local flow loss of the hydraulic oil can be further reduced.

[0055] Specifically, Figure 1 As shown, a rounded corner portion 221 is provided at the top of the interior of the cylinder sleeve 240 .

[0056] In a further embodiment of the present invention, Figure 3 , 4 As shown, the height of the first oil chamber 210 is defined as h. The height h of the first oil chamber 210 gradually decreases as the diameter d increases. The diameter d gradually increases along the radial direction of the first oil chamber 210. The piecewise function expression is:

[0057]

[0058] Among them, H is the distance between the bottom wall 2312 and the end of the second inclined side wall 2311 away from the bottom wall 2312, α1 is the cone angle of the first cone 421, α2 is the angle between the two first inclined side walls 431, α3 is the angle between the two inclined sections 2313, D1 is the diameter of the end of the first inclined side wall 431 away from the protrusion 420, D2 is the diameter of the bottom of the first cone 421, D3 is the diameter of the connection between the second inclined side wall 2311 and the bottom wall 2312, and D4 is the diameter of the connection between the inclined section 2313 and the rounded section 2314. The first oil chamber 210 adopts the above design, which can greatly reduce the flow dead zone of the hydraulic oil and make the flow rate of the hydraulic oil more uniform.

[0059] In a further embodiment of the present invention, Figure 1 , 5As shown in FIGS. 6 , the oil distribution plate 400 includes an oil distribution portion 440 and a support portion 450. The oil distribution portion 440 is located in the support portion 450. The oil outlet channel 410, the first concave cavity 430 and the protrusion 420 are all located on the oil distribution portion 440. The support portion 450 abuts against the cylinder body 230. The diameter D7 of the oil distribution portion 440 is 1 / 3 to 2 / 3 times the diameter D6 of the oil distribution plate 400. The oil distribution plate 400 adopts the above design, which can reduce the volume of the first oil chamber 210 and increase the area of ​​the support portion 450. The reduction in the volume of the first oil chamber 210 can reduce the filling amount of the hydraulic oil, thereby reducing the negative impact of the compressibility of the hydraulic oil on the volumetric efficiency of the compressor under high pressure conditions. The increase in the area of ​​the support portion 450 can enhance the stability of the oil distribution plate 400 itself and reduce the deformation of the oil distribution plate 400. Specifically, D7=1 / 2D6, or D7 can adopt other sizes if the strength requirements of the oil distribution plate and the arrangement of other functional holes are met.

[0060] In a further embodiment of the present invention, Figure 3 As shown, the central axis of the oil outlet channel 410 is perpendicular to the first inclined side wall 431, so that the oil outlet channel 410 is perpendicular to the second side 431. The oil outlet channel 410 is designed to reduce the component of the hydraulic oil flow rate in the direction perpendicular to the surface of the diaphragm 300, thereby preventing the hydraulic oil flow rate from being too high and causing impact on the diaphragm 300.

[0061] In a further embodiment of the present invention, Figure 3 , 5 As shown, the oil distribution plate 400 is provided with a plurality of circles of oil outlet groups 460 spaced apart in the radial direction of the oil distribution plate 400, and each circle of the oil outlet group 460 includes a plurality of oil outlet channels 410 spaced apart in the circumferential direction of the oil distribution plate 400. On the horizontal projection plane, the oil outlet group 460 located in the innermost circle is located outside the piston 500, and the sum of the flow areas of the plurality of oil outlet channels 410 is S1, and the area of ​​the piston hole 220 is S2, and S1 is 1.5 to 2.5 times of S2. The oil distribution plate 400 has a larger flow area, and the flow rate of the hydraulic oil flowing through the oil outlet channel 410 can be reduced.

[0062] Specifically, Figure 5 As shown, the oil outlet channel 410 includes a plurality of through-flow grooves 411 and a plurality of through-flow holes 412; the oil outlet group 460 may all be through-flow holes 412 or through-flow grooves 411; or it may be composed of a plurality of through-flow grooves 411 and a plurality of through-flow holes 412, a through-flow hole 412 being arranged between two adjacent through-flow grooves 411, and a through-flow area S1 formed by the plurality of through-flow grooves 411 and the plurality of through-flow holes 412 is twice the area of ​​the piston hole 220.

[0063] Specifically, Figure 3 , 5As shown, “on the horizontal projection plane, the oil outlet group 460 located in the innermost circle is located outside the piston 500 ” means: the diameter D8 of the oil outlet group 460 located in the innermost circle is larger than the diameter of the piston hole 220 ; the oil outlet group 460 located in the innermost circle includes a plurality of flow holes 410 .

[0064] In some embodiments of the present invention, Figure 1 , 7 As shown, the top of the oil distribution plate 400 has an oil guide groove 480 for guiding the hydraulic oil to the edge 471 of the second oil chamber 470. The oil guide groove 480 can prevent the hydraulic oil from being insufficient at the larger diameter portion of the second oil chamber 470.

[0065] Specifically, Figure 7 As shown, the oil guide groove 480 may be provided in plurality, and the plurality of oil guide grooves 480 are arranged at intervals along the circumferential direction of the oil distribution plate 400 .

[0066] In a further embodiment of the present invention, Figure 7 As shown, the oil distribution plate 400 is provided with an oil overflow hole 401 and an oil replenishing hole 402 at the edge 471 corresponding to the second oil chamber 470, as shown in FIG. Figure 1 As shown, the support assembly 200 has an oil overflow channel 232 and an oil replenishment channel 233 , the oil overflow hole 401 is connected to the oil overflow channel 232 , and the oil replenishment hole 402 is connected to the oil replenishment channel 233 .

[0067] By providing the oil overflow hole 401, the bubbles generated by the continuous pressurization and depressurization of the hydraulic oil can be discharged from the oil overflow hole 401 together with the hydraulic oil. Therefore, the negative impact of the bubbles in the hydraulic oil at high speed can be reduced, and the volumetric efficiency can be improved.

[0068] During operation, the hydraulic oil in the second oil chamber 470 can be discharged to the outside of the support assembly 200 through the oil overflow hole 401 and the oil overflow channel 232 to achieve oil overflow; the external hydraulic oil can also enter the second oil chamber 470 through the oil replenishment channel 233 and the oil replenishment hole 402 to achieve oil replenishment.

[0069] Specifically, Figure 1 As shown, the oil overflow channel 232 and the oil replenishment channel 233 are arranged on the cylinder body 230; Figure 7As shown, an annular air inlet groove 403 is provided at the edge 471 of the second oil chamber 470 of the oil distribution plate 400, and the annular air inlet groove 403 is connected to one end of the multiple oil inlet grooves 480 away from the middle of the oil distribution plate 400; the oil overflow hole 401 can be set on one of the oil inlet grooves 480, the oil replenishing hole 402 can be set on another oil inlet groove 480, and the oil overflow hole 401 and the oil replenishing hole 402 can also be set on the same oil inlet groove 480; the oil overflow channel 232 and the oil replenishing channel 233 can both be connected to an external pipeline, and a valve can be set on the pipeline, and then the opening and closing of the oil overflow channel 232 and the opening and closing of the oil replenishing channel 233 are controlled respectively by the two valves.

[0070] The manufacturing method of the high-speed diaphragm compressor double-cone oil chamber structure of the second embodiment of the present invention is used to obtain the high-speed diaphragm compressor double-cone oil chamber structure of the first embodiment, and the manufacturing method comprises the following steps:

[0071] like Figure 4 , 8 As shown, step 1: determine the diameter D5 of the piston 500, the cone angle α4 of the second cone 510 and the cone angle α1 of the first cone 421, α4 is 160° to 180°, α1 is 140° to 160°, and the diameter D2 of the bottom of the first cone 421 is equal to the diameter D5 of the piston 500; D5 is obtained by expression 2, which is:

[0072]

[0073] Among them, Q is the exhaust volume of the diaphragm compressor (m3 / s), n is the rotation speed of the crankshaft of the diaphragm compressor (rpm), and L is the stroke of the piston 500 (m). When designing, the user can obtain Q, n and L according to the parameters of the diaphragm compressor, and then obtain D5;

[0074] Step 2: Determine D1 and α2, α2 = 168° to 176°, the diameter D6 of the oil distribution plate 400 is greater than or equal to 2 times D1, and D6 is less than the diameter of the cylinder body 230; D1 is obtained by expression 3, which is:

[0075]

[0076] Where, Q is the exhaust volume of the diaphragm compressor (m3 / s), n is the speed of the crankshaft of the diaphragm compressor (rpm), and W 0 is the maximum deflection of the diaphragm 300 (mm), z is the deflection index of the diaphragm 300. When designing, the user can obtain Q, n, and W based on the parameters of the diaphragm compressor. 0 and z, and then D1 can be inferred, and then D6 can be obtained. D6 can also be the optimal D6 under the premise of meeting the requirements of floor space and installation;

[0077] Step 3: Determine α3, D4 and D3, α3 is 164° to 172°, D4 is 5mm to 10mm smaller than D1; obtain D3 by hydraulic oil fluid simulation and observation of the flow dead zone size of the hydraulic oil, specifically, D3 is 240mm;

[0078] Step 4: Set up a plurality of oil outlet channels 410 on the oil distribution plate 400 .

[0079] The double-cone oil chamber structure of the high-speed diaphragm compressor is designed by adopting the above method to prevent the occurrence of cavitation and provide stability for the operation of the high-speed diaphragm compressor.

[0080] In the description of this specification, the description with reference to the terms "some embodiments" or "it is conceivable that" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0081] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A double-cone oil chamber structure of a high-speed diaphragm compressor, comprising a cylinder head (100) and a support assembly (200), wherein the cylinder head (100) is mounted on the support assembly (200), a diaphragm (300) and an oil distribution plate (400) are arranged in sequence in the up-down direction between the support assembly (200) and the cylinder head (100), a first oil chamber (210) is arranged between the support assembly (200) and the bottom of the oil distribution plate (400), the oil distribution plate (400) has an oil outlet channel (410), and a second oil chamber (470) is arranged between the top of the oil distribution plate (400) and the diaphragm (300), characterized in that: The bottom of the oil distribution plate (400) has a protrusion (420) extending into the first oil chamber (210), and the protrusion (420) is in a first cone shape (421). The support assembly (200) has a piston hole (220) connected to the first oil chamber (210), and a piston (500) that can move up and down is arranged in the piston hole (220). The top of the piston (500) is in a second cone shape (510), and the first cone (421) and the second cone (510) are arranged opposite to each other.

2. The double-cone oil chamber structure of the high-speed diaphragm compressor according to claim 1 is characterized in that: The support assembly (200) comprises a cylinder body (230), the cylinder head (100) and the oil distribution plate (400) are both mounted on the cylinder body (230), the bottom of the oil distribution plate (400) comprises a first concave cavity (430), the longitudinal section of the first concave cavity (430) comprises two first inclined side walls (431), the protrusion (420) is located between the two first inclined side walls (431), the top of the cylinder body (230) comprises a second concave cavity (231) connected to the piston hole (220), the longitudinal section of the second concave cavity (231) comprises two second inclined side walls (2311) and a bottom wall (2312) located between the two second inclined side walls (2311), the first inclined side wall (431), the protrusion (420), the second inclined side wall (2311) and the bottom wall (2312) enclose the first oil chamber (210).

3. The double-cone oil chamber structure of the high-speed diaphragm compressor according to claim 2 is characterized in that: The second inclined side wall (2311) includes an inclined section (2313) and a rounded section (2314), and the two ends of the inclined section (2313) are respectively connected to the rounded section (2314) and the bottom wall (2312), and the top of the piston hole (220) has a rounded portion (221).

4. The double-cone oil chamber structure of the high-speed diaphragm compressor according to claim 3 is characterized in that: The height of the first oil chamber (210) is defined as h. The height h of the first oil chamber (210) first gradually increases and then gradually decreases along the increase of a diameter d. The diameter d gradually increases along the radial direction of the first oil chamber (210). The piecewise function expression 1 is: Wherein, H is the distance between the bottom wall (2312) and the end of the second inclined side wall (2311) away from the bottom wall (2312), α1 is the cone angle of the first cone (421), α2 is the angle between the two first inclined side walls (431), α3 is the angle between the two inclined sections (2313), D1 is the diameter of the end of the first inclined side wall (431) away from the protrusion (420), D2 is the diameter of the bottom of the first cone (421), D3 is the diameter of the connection between the second inclined side wall (2311) and the bottom wall (2312), and D4 is the diameter of the connection between the inclined section (2313) and the chamfered section (2314).

5. The double-cone oil chamber structure of a high-speed diaphragm compressor according to any one of claims 2 to 4, characterized in that: The central axis of the oil outlet channel (410) is perpendicular to the first inclined side wall (431).

6. The double-cone oil chamber structure of a high-speed diaphragm compressor according to any one of claims 2 to 4, characterized in that: The oil distribution plate (400) comprises an oil distribution part (440) and a supporting part (450); the oil distribution part (440) is located inside the supporting part (450); the oil outlet channel (410), the first concave cavity (430) and the protrusion (420) are all located on the oil distribution part (440); the supporting part (450) abuts against the cylinder body (230); and a diameter D7 of the oil distribution part (440) is 1 / 3 to 2 / 3 times the diameter D6 of the oil distribution plate (400).

7. The double-cone oil chamber structure of a high-speed diaphragm compressor according to any one of claims 1 to 4, characterized in that: The oil distribution plate (400) is formed with a plurality of oil outlet groups (460) arranged at intervals along the radial direction of the oil distribution plate (400), and each circle of the oil outlet group (460) includes a plurality of oil outlet channels (410) arranged at intervals along the circumferential direction of the oil distribution plate (400). On a horizontal projection plane, the oil outlet group (460) located in the innermost circle is located outside the piston (500), and the sum of the flow areas of the plurality of oil outlet channels (410) is S1. The area of ​​the piston hole (220) is S2, and S1 is 1.5 to 2.5 times of S2.

8. The double-cone oil chamber structure of the high-speed diaphragm compressor according to claim 1 is characterized in that: The top of the oil distribution plate (400) is provided with an oil guide groove (480) for guiding the hydraulic oil to the edge (471) of the second oil chamber (470).

9. The double-cone oil chamber structure of the high-speed diaphragm compressor according to claim 8 is characterized in that: The oil distribution plate (400) is provided with an oil overflow hole (401) and an oil replenishing hole (402) at the edge (471) corresponding to the second oil chamber (470); the support assembly (200) has an oil overflow channel (232) and an oil replenishing channel (233); the oil overflow hole (401) is connected to the oil overflow channel (232); and the oil replenishing hole (402) is connected to the oil replenishing channel (233).

10. A method for manufacturing a double-cone oil chamber structure of a high-speed diaphragm compressor, for obtaining the double-cone oil chamber structure of a high-speed diaphragm compressor according to claim 4, characterized in that: The following steps are involved: Step 1: Determine the diameter D5 of the piston (500), the cone angle α4 of the second cone (510) and the cone angle α1 of the first cone (421), α4 is 160° to 180°, α1 is 140° to 160°, and the diameter D2 of the bottom of the first cone (421) is equal to the diameter D5 of the piston (500); D5 is obtained by expression 2, which is: Wherein, Q is the exhaust volume of the diaphragm compressor (m3 / s), n is the rotation speed of the crankshaft of the diaphragm compressor (rpm), and L is the stroke of the piston (500) (m); Step 2: Determine the D1 and the α2, α2 = 168° to 176°, the diameter D6 of the oil distribution plate (400) is greater than or equal to 2 times D1; ​​D1 is obtained by expression 3, which is: Wherein, Q is the exhaust volume of the diaphragm compressor (m3 / s), n is the rotation speed of the crankshaft of the diaphragm compressor (rpm), W0 is the maximum deflection of the diaphragm (300) (mm), and z is the deflection index of the diaphragm (300); Step 3: Determine the α3, D4 and D3, α3 is 164° to 172°, D4 is 5mm to 10mm smaller than D1, and D3 is 240mm; Step 4: A plurality of oil outlet channels (410) are provided on the oil distribution plate (400).

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