A dual rotor pump body assembly and dual rotor compressor

Abstract

The application provides a double-rotor pump body assembly and a double-rotor compressor, and relates to the technical field of compressors.The application solves the technical problem that in the prior art, when suction liquid is compressed in the pump body assembly, deformation of the crankshaft can cause damage to the pump body assembly.The double-rotor pump body assembly comprises a first cylinder, a second cylinder, a partition plate and a crankshaft, the inner wall of an upper cavity and / or a lower cavity forms a first inner circle;the crankshaft is eccentrically provided with a first roller structure and a second roller structure, the first roller structure and the second roller structure are symmetrically arranged, when the crankshaft rotates, the trajectory line of the position with the longest distance between the edge of the first roller structure and / or the second roller structure rotating and the center axis of the crankshaft is a trajectory circle;the crankshaft is eccentrically installed on the first cylinder and the second cylinder, so that the maximum gap Pb between the trajectory circle and the inner wall of the upper cavity and / or the lower cavity is greater than P.The application is used for providing a double-rotor pump body assembly and a double-rotor compressor which can avoid damage to the pump body assembly caused by interference wear of parts.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressor, in particular to a double rotor pump body assembly and double rotor compressor. BACKGROUND

[0002] The pump body assembly is used for compressing gas, in order to ensure the compression capacity and reduce leakage, the assembly gap is usually at the level of 0.01mm, so that liquid is not allowed to be compressed in the pump body assembly. Due to the particularity of some application occasions, it is impossible to avoid that the compressor sucks liquid, when the liquid is compressed, the crankshaft will be subjected to overloading pressure and be deformed.

[0003] The existing double rotor compressor includes a distributor and a pump body assembly, the pump body assembly includes a first flange, a first cylinder, a partition plate, a second cylinder, a first roller, a first sliding vane, a second cylinder, a second roller, a second sliding vane, a second flange and the like, the crankshaft passes through the first flange, the first roller, the partition plate, the second roller, the second flange and the like, and the first roller and the second roller are respectively installed in the inner circle of the first cylinder and the second cylinder.

[0004] As shown in Figure 1 When the pump body assembly sucks gas with liquid or all liquid, the liquid enters the compression chamber for compression, because the liquid is poor in compressibility and difficult to be discharged in time, the liquid will accumulate in the compression chamber to hinder the operation of the first roller and the crankshaft and the second roller and the crankshaft, the crankshaft will be subjected to strong resistance and be greatly deformed, under the influence of the deformation of the crankshaft, the first roller and the second roller can interfere with and collide with the inner circle of the cylinder, and in severe cases, the interference and collision can cause the parts to be worn and damaged, resulting in damage of the pump body assembly. SUMMARY

[0005] The present application provides a double rotor pump body assembly and double rotor compressor to solve the technical problem that the deformation of the crankshaft caused by the compression of liquid in the pump body assembly with liquid in the suction gas can damage the pump body assembly. The preferred technical solutions in the many technical solutions provided by the present application can produce many technical effects, which are described in detail below.

[0006] To achieve the above-mentioned purpose, the present application provides the following technical solutions:

[0007] The double rotor pump body assembly provided by the present application comprises:

[0008] The first cylinder has an upper cavity body;

[0009] The second cylinder has a lower cavity body;

[0010] A partition is arranged between the first cylinder and the second cylinder, and an inner wall of the upper cavity and / or the lower cavity forms a first inner circle, which is concentric with an outer circle of the first cylinder and / or the second cylinder;

[0011] and a crankshaft, which is eccentrically arranged with a first roller structure and a second roller structure, the first roller structure is arranged in the upper cavity, the second roller structure is arranged in the lower cavity, and the first roller structure and the second roller structure are symmetrically arranged, when the crankshaft rotates, a locus of a position with the longest distance between the edge of the first roller structure and / or the second roller structure and the central axis of the crankshaft is a locus circle;

[0012] The crankshaft is eccentrically mounted on the first cylinder and the second cylinder, so that the maximum gap Pb between the locus circle and the inner wall of the upper cavity and / or the lower cavity is greater than P, and P=(dh-dr) / 2-e;

[0013] Wherein: dh is the diameter of the first inner circle, dr is the diameter of the locus circle, and e is the distance between the first roller structure and / or the second roller structure and the central axis of the crankshaft.

[0014] Optionally, a second inner arc is arranged on the inner wall of the upper cavity and / or the lower cavity, and the second inner arc is arranged on the side of the maximum gap between the locus circle and the upper cavity and / or the lower cavity.

[0015] Optionally, the maximum gap Pb between the locus circle and the inner wall of the upper cavity and / or the lower cavity is greater than or equal to v*2*10 -9 , v=3.14*(dh*dh-dr*dr)*h,

[0016] Wherein: h is the height of the cylinder.

[0017] Optionally, the maximum gap Pb between the locus circle and the inner wall of the upper cavity and / or the lower cavity is less than or equal to v*6*10 -9 .

[0018] Optionally, the crankshaft is eccentrically mounted on the first cylinder and the second cylinder from the b point to the a point direction, the maximum gap between the locus circle and the inner wall of the upper cavity and / or the lower cavity is the b point, and the minimum gap between the locus circle and the inner wall of the upper cavity and / or the lower cavity is the a point.

[0019] Optionally, a first sliding groove is arranged on the first cylinder, and a first sliding plate is arranged in the first sliding groove, and the first sliding plate slides along the first sliding groove under the action of a spring and / or the first roller structure;

[0020] A second sliding slot is arranged on the second cylinder, and a second sliding plate is arranged in the second sliding slot and slides along the second sliding slot under the action of a spring and / or the second roller structure;

[0021] The angle range between the center of the first cylinder and a point in the first cylinder and the center of the first sliding plate is a1, the angle range between the center of the first cylinder and a point in the first cylinder and the center of the first sliding plate is b1, and a1 and b1 are symmetrically distributed;

[0022] The angle range between the center of the second cylinder and a point in the second cylinder and the center of the second sliding plate is a1, the angle range between the center of the second cylinder and a point in the second cylinder and the center of the second sliding plate is b1, and a1 and b1 are symmetrically distributed.

[0023] Optionally, the first flange and the second flange are further included, the first flange is provided with a first mounting hole, the first connecting piece connects the first flange and the first cylinder through the first mounting hole, the second flange is provided with a second mounting hole, the second connecting piece connects the second flange and the second cylinder through the second mounting hole, and the crankshaft is fixed on the first flange and the second flange;

[0024] The first mounting hole and the second mounting hole are eccentrically arranged, so that the crankshaft is eccentrically mounted on the cylinder from the b point to the a point.

[0025] Optionally, the first roller structure includes a first eccentric cylinder and a first roller, and the second roller structure includes a second eccentric cylinder and a second roller, the first eccentric cylinder and the second eccentric cylinder are arranged on the crankshaft, the first roller is arranged on the first eccentric cylinder, and the second roller is arranged on the second eccentric cylinder.

[0026] Optionally, the first cylinder is provided with a first air inlet hole in communication with the upper cavity;

[0027] The second cylinder is provided with a second air inlet hole in communication with the lower cavity;

[0028] The partition plate is arranged between the first cylinder and the second cylinder to form a gas storage cavity;

[0029] The gas storage cavity has an air inlet, a first air outlet hole and a second air outlet hole in communication with the gas storage cavity; the first air outlet hole and the second air outlet hole are arranged on opposite sides of the gas storage cavity, and the first air inlet hole and the second air inlet hole are respectively located on two sides of the double-rotor pump body assembly axis;

[0030] The first air outlet hole and the first air inlet hole are in communication, and the second air outlet hole and the second air inlet hole are in communication;

[0031] External gas enters the gas storage cavity through the gas inlet, and the gas in the gas storage cavity enters the upper cavity through the first gas outlet and the first gas suction hole, and enters the lower cavity through the second gas outlet and the second gas suction hole.

[0032] A double-rotor compressor comprising a distributor and a double-rotor pump body assembly as described above.

[0033] The double-rotor pump body assembly and the double-rotor compressor provided by the application have the following beneficial effects: the double-rotor pump body assembly and the double-rotor compressor comprise a first cylinder, a second cylinder, a partition plate and a crankshaft, the crankshaft is provided with a first roller structure and a second roller structure, the first roller structure and the second roller structure are both eccentrically arranged and symmetrically distributed, the first roller structure and the second roller structure form a track circle when the crankshaft rotates, the first roller structure and the second roller structure form track circles of the same size, the inner walls of an upper cavity in the first cavity and a lower cavity in the second cavity form a second inner circle of the same size and concentric circles, when the crankshaft is eccentrically arranged on the first cylinder and the second cylinder, the gap between the track circle and the first inner circle changes due to the change of the center of the crankshaft, the first side gap becomes larger and the second side gap becomes smaller, when liquid enters the compression cavity for compression, the crankshaft deforms to the first side due to the resistance on the second side, and the gap between the first roller structure and the first inner circle of the upper cavity and the gap between the second roller structure and the first inner circle of the lower cavity increase due to the larger first side gap, so that the deformation amount of the crankshaft is increased, and the probability of interference and collision is effectively reduced, and the problem of damage of the pump body assembly caused by interference and wear of parts is avoided. BRIEF DESCRIPTION OF DRAWINGS

[0034] In order to more clearly illustrate the technical solutions in the embodiments of the application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or the prior art description. Obviously, the drawings in the following description only show some embodiments of the application, and for those skilled in the art, other drawings can also be obtained from these drawings without creative labor.

[0035] Figure 1 is a structural schematic diagram of the prior art of the application;

[0036] Figure 2 is a structural schematic diagram of the application;

[0037] Figure 3 is a B-B sectional view of the application;

[0038] Figure 4 is a wear amount test result analysis diagram of the application.

[0039] 100, first flange; 110, first cylinder; 120, second cylinder; 130, partition; 140, second flange; 150, crankshaft; 160, first roller structure; 170, first eccentric cylinder; 180, first roller; 190, second roller structure; 200, second eccentric cylinder; 210, second roller; 220, first inner circle; 230, second inner circle; 240, track circle; 250, first sliding groove; 260, first sliding piece. DETAILED DESCRIPTION

[0040] The content of the present application and the difference between the present application and the prior art can be understood below with reference to the accompanying drawings Figures 1-4 and the text. The technical solutions of the present application (including the preferred technical solutions) are described in further detail below by means of the accompanying drawings and by listing some optional embodiments of the present application. It should be noted that any technical feature or any technical solution in the present embodiment is one or several of multiple optional technical features or optional technical solutions. In order to simplify the description, all the alternative technical features and alternative technical solutions of the present application cannot be listed in the present document, and it is not convenient to emphasize that the implementation mode of each technical feature is one of multiple optional implementation modes. Therefore, the person skilled in the art should know that any technical means provided by the present application can be replaced, or any two or more technical means or technical features provided by the present application can be combined to obtain a new technical solution. Any technical feature and any technical solution in the present embodiment do not limit the protection scope of the present application, and the protection scope of the present application should include any alternative technical solution that can be thought of by the person skilled in the art without creative labor, and the new technical solution obtained by the person skilled in the art by combining any two or more technical means or technical features provided by the present application.

[0041] In the description of the present application, it should be noted that, unless otherwise specified, the meaning of "multiple" is two or more than two; the orientation or positional relationship indicated by the terms "upper", "lower", "left", "right", "inner", "outer", "front end", "rear end", "head", "tail" and the like is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application. In addition, the terms "first", "second", "third" and the like are only for description purposes and cannot be understood as indicating or implying relative importance.

[0042] In the description of the present application, it is also necessary to explain that, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connecting" should be understood in a broad sense, for example, it can be fixed connection, or detachable connection, or integrally connected, it can be mechanical connection, or electrical connection, it can be directly connected, or indirectly connected through intermediate medium. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0043] The present application provides a double-rotor pump body assembly and a double-rotor compressor which avoid part interference wear and damage to the pump body assembly.

[0044] The following will be described in combination with Figures 1-4 The technical solutions provided by the present application will be described in more detail.

[0045] The present application provides a double-rotor pump body assembly, comprising:

[0046] The first cylinder 110 has an upper cavity;

[0047] The second cylinder 120 has a lower cavity;

[0048] The partition plate 130 is arranged between the first cylinder 110 and the second cylinder 120, the inner wall of the upper cavity and / or the lower cavity forms a first inner circle 220, and the first inner circle 220 is concentric with the outer circle of the first cylinder 110 and / or the second cylinder 120;

[0049] And the crankshaft 150, the first roller structure 160 and the second roller structure 190 are eccentrically arranged on the crankshaft 150, the first roller structure 160 is arranged in the upper cavity, the second roller structure 190 is arranged in the lower cavity, and the first roller structure 160 and the second roller structure 190 are symmetrically arranged, when the crankshaft 150 rotates, the longest position of the edge of the first roller structure 160 and / or the second roller structure 190 from the center axis of the crankshaft 150 is the trajectory circle 240;

[0050] The crankshaft 150 is eccentrically mounted on the first cylinder 110 and the second cylinder 120, so that the maximum gap Pb between the trajectory circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is greater than P, P=(dh-dr) / 2-e;

[0051] Wherein: dh is the diameter of the first inner circle 220, dr is the diameter of the trajectory circle 240, and e is the distance of the first roller structure 160 and / or the second roller structure 190 from the center of the long axis of the crankshaft 150.

[0052] The double-rotor pump body assembly provided by the application comprises a first cylinder 110, a second cylinder 120, a partition plate 130 and a crankshaft 150, the crankshaft 150 is provided with a first roller structure 160 and a second roller structure 190, the first roller structure 160 and the second roller structure 190 are both eccentrically arranged and symmetrically distributed, the first roller structure 160 and the second roller structure 190 form a track circle 240 when the crankshaft 150 rotates, the first roller structure 160 and the second roller structure 190 form the track circle 240 with the same size, the inner wall of the upper cavity in the first cavity and the inner wall of the lower cavity of the second cavity form a second inner circle with the same size and concentric, when the crankshaft 150 is eccentrically installed on the first cylinder 110 and the second cylinder 120, the gap between the track circle 240 and the first inner circle 220 changes due to the change of the center of the crankshaft 150, the first side gap becomes larger and the second side gap becomes smaller, when the liquid enters the compression cavity for compression, the crankshaft 150 deforms to the first side under the resistance of the second side, and the gap between the first roller structure 160 and the first inner circle 220 of the upper cavity and the gap between the second roller structure 190 and the first inner circle 220 of the lower cavity increase due to the larger first side gap, so that the deformation amount of the crankshaft 150 is increased, thereby effectively reducing the probability of interference and collision and avoiding the problem of damage of the pump body assembly caused by interference wear of parts.

[0053] It can be understood that the track circle 240 is a track line formed by the rotation of the outer edge of the maximum distance between the first roller structure 160 or the second roller structure 190 and the center of the crankshaft 150.

[0054] According to the test of a certain H98z compressor, v=49x10 6 mm3, p=0.03-0.04mm, the wear amount corresponding to different gaps under specific working conditions is as shown in the table, and it can be seen that the larger the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120, the more effectively the wear amount of the crankshaft 150 and the wear amount of the B point are reduced. Figure 4

[0055] In some embodiments of the application, the crankshaft 150 is eccentrically installed on the first cylinder 110 and the second cylinder 120 from the b point to the a point, the maximum gap between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is the b point, and the minimum gap between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is the a point.

[0056] ​In some embodiments of the present application, the crankshaft 150 is eccentrically mounted on the first cylinder 110 and the second cylinder 120 from the b point to the a point, so that the maximum gap of the b point trajectory circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120, due to the eccentric mounting of the crankshaft 150, can make Pb>P, P=(dh-dr) / 2-e, thereby increasing the gap between the first roller structure 160 and the first inner circle 220 of the upper cavity, and the gap between the second roller structure 190 and the first inner circle 220 of the lower cavity, thereby increasing the deformation of the crankshaft 150, thereby effectively reducing the probability of interference and collision, avoiding the problem of damage to the double-rotor pump body assembly caused by part interference and wear.

[0057] Further, the first flange 100 and the second flange 140 are further included, the first mounting hole is arranged on the first flange 100, the first connecting piece connects the first flange 100 and the first cylinder 110 through the first mounting hole, the second mounting hole is arranged on the second flange 140, and the second connecting piece connects the second flange 140 and the second cylinder 120 through the second mounting hole, and the crankshaft 150 is fixed on the first flange 100 and the second flange 140.

[0058] The first mounting hole and the second mounting hole are eccentrically arranged to eccentrically mount the crankshaft 150 on the cylinder from the b point to the a point.

[0059] In this further improved scheme, since the crankshaft 150 is fixed on the first flange 100 and the second flange 140, the crankshaft 150 is eccentrically mounted on the first cylinder 110 and the second cylinder 120, and by arranging the first mounting hole and the second mounting hole on the first flange 100 and the second flange 140 respectively, the eccentric mounting of the crankshaft 150 can be realized by changing the positions of the first mounting hole and the second mounting hole.

[0060] Further, the first sliding groove 250 is arranged on the first cylinder 110, the first sliding piece 260 is arranged in the first sliding groove 250, and the first sliding piece 260 slides along the first sliding groove 250 under the action of the spring and / or the first roller structure 160.

[0061] The second sliding groove is arranged on the second cylinder 120, the second sliding piece is arranged in the second sliding groove, and the second sliding piece slides along the second sliding groove under the action of the spring and / or the second roller structure 190.

[0062] Taking the center of the cylinder as the axis, the included angle range between the a point and the center of the first sliding piece 260 or the second sliding piece is a1, the included angle range between the b point and the center of the first sliding piece 260 or the second sliding piece is b1, and a1 and b1 are symmetrically distributed.

[0063] In the further improved scheme, generally the crankshaft 150 has the maximum resistance in the a1 range, forcing the crankshaft 150 to deform to the b1 range, and in the double rotor pump body assembly, when the first roller structure 160 of the first cylinder 110 runs in the a1 range, the second roller structure 190 in the second cylinder 120 is just running in the b1 range, due to the influence of the double rotor structure, the deformed second roller structure 190 may interfere and collide with the first inner circle 220 of the second cylinder 120, and may even cause part interference wear, by eccentrically arranging the crankshaft 150, the maximum gap value between the track circle 240 of the second roller structure 190 and the first inner circle 220 of the second cylinder 120 is increased, the probability of wear between the second roller structure 190 and the second cylinder 120 is reduced, and the problem of part interference wear causing damage to the double rotor pump body assembly is avoided.

[0064] In some embodiments of the present application, a second inner arc 230 is arranged on the inner wall of the first inner circle 220 on the side of the maximum gap between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120.

[0065] In some embodiments of the present application, by arranging the second inner arc 230 on the inner wall of the first inner circle 220, the maximum gap between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is increased, further ensuring that the gap between the first roller structure 160 and the inner wall of the upper cavity and the gap between the second roller structure 190 and the inner wall of the lower cavity are increased, thereby increasing the deformation amount of the crankshaft 150, effectively reducing the probability of interference and collision, and avoiding the problem of part interference wear causing damage to the pump body assembly.

[0066] It can be understood that the diameter of the second inner arc 230 can be greater than, equal to, or less than the diameter of the first inner circle 220, and the second inner arc 230 is offset to the outside of the first inner circle 220, so as to increase the maximum gap between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120.

[0067] In some embodiments of the present application, the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is greater than or equal to v*2*10 -9 , v = 3.14*(dh*dh-dr*dr)*h,

[0068] Wherein: h is the height of the cylinder.

[0069] In some embodiments of the present application, the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is greater than or equal to v*2*10 -9时 , v=3.14*(dh*dh-dr*dr)*h, which can solve the problem of interference wear, effectively reduce the wear of the crankshaft 150, and produce good results.

[0070] In further embodiments of the present application, the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is less than or equal to v*6*10 -9 .

[0071] In this further improvement, in order to ensure the working performance of the double-rotor pump body assembly, the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is less than or equal to v*6*10 -9 .

[0072] Embodiment 1:

[0073] The present application provides a double-rotor pump body assembly, comprising:

[0074] a first flange 100;

[0075] a first cylinder 110 having an upper cavity and a first air inlet hole communicating with the upper cavity;

[0076] a second cylinder 120 having a lower cavity and a second air inlet hole communicating with the lower cavity, the inner wall of the upper cavity and / or the lower cavity forming a first inner circle 220, the first inner circle 220 being concentric with the outer circle of the first cylinder 110 and / or the second cylinder 120;

[0077] a partition plate 130 arranged between the first cylinder 110 and the second cylinder 120 and forming a gas storage cavity;

[0078] the gas storage cavity having an air inlet hole, a first air outlet hole and a second air outlet hole communicating with the gas storage cavity; the first air outlet hole and the second air outlet hole being oppositely arranged on both sides of the gas storage cavity, and the first air inlet hole and the second air inlet hole being correspondingly located on both sides of the axis of the double-rotor pump body assembly;

[0079] the first air outlet hole and the first air inlet hole being in communication; and the second air outlet hole and the second air inlet hole being in communication;

[0080] ambient gas enters the gas storage cavity through the air inlet hole, and the gas in the gas storage cavity enters the upper cavity through the first air outlet hole and the first air inlet hole, and enters the lower cavity through the second air outlet hole and the second air inlet hole;

[0081] The second flange 140;

[0082] The crankshaft 150 is eccentrically installed on the first cylinder 110 and the second cylinder 120, so that the gap between the track circle 240 and the first inner circle 220 is the maximum value Pb>P, P=(dh-dr) / 2-e.

[0083] Wherein: dh is the diameter of the first inner circle 220, dr is the diameter of the track circle 240, and e is the distance between the first roller structure 160 and / or the second roller structure 190 and the center of the crankshaft 150 long axis.

[0084] Wherein: dh is the diameter of the first inner circle 220, dr is the diameter of the track circle 240, and e is the distance between the first roller structure 160 and / or the second roller structure 190 and the center of the crankshaft 150 long axis.

[0085] Specifically, the first flange 100 is provided with a first mounting hole, and the first connecting piece connects the first flange 100 and the first cylinder 110 through the first mounting hole. The second flange 140 is provided with a second mounting hole, and the second connecting piece connects the second flange 140 and the second cylinder 120 through the second mounting hole. The crankshaft 150 is fixed on the first flange 100 and the second flange 140.

[0086] The first mounting hole and the second mounting hole are eccentrically arranged, so that the crankshaft 150 is eccentrically installed on the cylinder.

[0087] Further, the first cylinder 110 is provided with a first sliding groove 250, and the first sliding groove 250 is provided with a first sliding piece 260. The first sliding piece 260 slides along the first sliding groove 250 under the action of the spring and / or the first roller structure 160.

[0088] The second cylinder 120 is provided with a second sliding groove, and the second sliding groove is provided with a second sliding piece. The second sliding piece slides along the second sliding groove under the action of the spring and / or the second roller structure 190.

[0089] The angle range of the a point in the first cylinder 110 and the center of the first sliding vane 260 is a1, the angle range of the b point in the first cylinder 110 and the center of the first sliding vane 260 is b1, and a1 and b1 are symmetrically distributed.

[0090] The angle range of the a point in the second cylinder 120 and the center of the second sliding vane is a1, the angle range of the b point in the second cylinder 120 and the center of the second sliding vane is b1, and a1 and b1 are symmetrically distributed.

[0091] Embodiment 2:

[0092] The difference between the embodiment 2 and the embodiment 1 is that the second inner arc 230 is arranged on the inner wall of the first inner circle 220 on the side of the maximum gap between the track circle 240 and the first inner circle 220.

[0093] It can be understood that the second inner arc 230 can be a semicircle arc or a quarter circle arc or other special-shaped arcs.

[0094] Further, the maximum gap v*6*10 between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 -9 ≥Pb≥v*2*10 -9 , v = 3.14 * (dh*dh-dr*dr) * h,

[0095] Wherein, h is the height of the cylinder.

[0096] In some embodiments of the present application, when the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is greater than or equal to v*2*10 -9 , v = 3.14 * (dh*dh-dr*dr) * h, the problem of interference wear can be solved, the wear of the crankshaft 150 is effectively reduced, and good results are produced.

[0097] In order to ensure the working performance of the double-rotor pump body assembly, the maximum gap Pb between the track circle 240 and the inner wall of the upper cavity 110 and / or the lower cavity 120 is less than or equal to v*6*10 -9 .

[0098] Embodiment 3:

[0099] The difference between the embodiment 3 and the embodiment 1 is that when the crankshaft 150 is installed, according to experience, the first connecting piece and the second connecting piece are driven to move to eccentrically install the crankshaft 150 on the cylinder.

[0100] It is understood that when the first connecting member and the second connecting member are a bolt or a screw, the bolt or the screw is tightened, and an eccentric force is applied to eccentrically mount the crankshaft 150 on the first cylinder 110 and the second cylinder 120.

[0101] In the description of the present specification, the description referring to the terms "example", "embodiment", or "some embodiments" or the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In the present specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Also, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in an appropriate manner.

[0102] Of course, the present invention is not limited to the above-described embodiments, and those skilled in the art can make equivalent modifications or substitutions without departing from the spirit of the present invention, and these equivalent modifications or substitutions are included in the scope defined by the claims of the present application.

Claims

1. A dual-rotor pump body assembly, characterized in that, include: The first cylinder has an upper cavity; The second cylinder has a lower chamber; The partition, the inner wall of the upper cavity and / or the lower cavity forms a first inner circle, the first inner circle being concentric with the outer circle of the first cylinder and / or the second cylinder; The crankshaft has a first roller structure and a second roller structure eccentrically arranged on it. The first roller structure is arranged in the upper cavity, and the second roller structure is arranged in the lower cavity. The first roller structure and the second roller structure are symmetrically arranged. When the crankshaft rotates, the trajectory line of the position where the edge of the first roller structure and / or the second roller structure is the longest distance from the central axis of the crankshaft is a trajectory circle. The crankshaft is eccentrically mounted on the first cylinder and the second cylinder so that the maximum gap between the trajectory circle and the inner wall of the upper cavity and / or the lower cavity is Pb > P, P = (dh - dr) / 2 - e; Wherein: dh is the diameter of the first inner circle, dr is the diameter of the trajectory circle, and e is the distance between the first roller structure and / or the second roller structure and the center of the crankshaft major axis; A second inner arc is provided on the inner wall of the upper cavity and / or the lower cavity, and the second inner arc is located on the side of the maximum gap between the trajectory circle and the upper cavity and / or the lower cavity; The maximum gap between the trajectory circle and the inner wall of the upper cavity and / or lower cavity is Pb ≥ v*2*10. -9 v = 3.14 * (dh * dh - dr * dr) * h Where: h is the cylinder height.

2. The dual-rotor pump assembly according to claim 1, characterized in that, The maximum gap between the trajectory circle and the inner wall of the upper cavity and / or lower cavity is Pb≤v*6*10. -9 .

3. The dual-rotor pump body assembly according to claim 1, characterized in that, The crankshaft is eccentrically mounted on the first cylinder and the second cylinder from point b to point a. The maximum gap between the trajectory circle and the inner wall of the upper cavity and / or the lower cavity is point b, and the minimum gap between the trajectory circle and the inner wall of the upper cavity and / or the lower cavity is point a.

4. The dual-rotor pump body assembly according to claim 3, characterized in that, A first slide groove is provided on the first cylinder, and a first slide plate is provided in the first slide groove. The first slide plate slides along the first slide groove under the action of a spring and / or the first roller structure. A second slide groove is provided on the second cylinder, and a second slide plate is provided in the second slide groove. The second slide plate slides along the second slide groove under the action of a spring and / or the second roller structure. With the center of the first cylinder as the axis, the angle between point a inside the first cylinder and the center of the first sliding vane is a1, and the angle between point b inside the first cylinder and the center of the first sliding vane is b1. a1 and b1 are symmetrically distributed. With the center of the second cylinder as the axis, the angle between point a inside the second cylinder and the center of the second sliding vane is a1, and the angle between point b inside the second cylinder and the center of the second sliding vane is b1. a1 and b1 are symmetrically distributed.

5. The dual-rotor pump body assembly according to claim 3, characterized in that, It also includes a first flange and a second flange. The first flange is provided with a first mounting hole. A first connector connects the first flange to the first cylinder through the first mounting hole. The second flange is provided with a second mounting hole. A second connector connects the second flange to the second cylinder through the second mounting hole. The crankshaft is fixed on the first flange and the second flange. The first mounting hole and the second mounting hole are eccentrically positioned so that the crankshaft is eccentrically mounted on the cylinder from point b to point a.

6. The dual-rotor pump body assembly according to any one of claims 1-5, characterized in that, The first roller structure includes a first eccentric cylinder and a first roller, and the second roller structure includes a second eccentric cylinder and a second roller. The first eccentric cylinder and the second eccentric cylinder are disposed on the crankshaft, the first roller is disposed on the first eccentric cylinder, and the second roller is disposed on the second eccentric cylinder.

7. The dual-rotor pump body assembly according to any one of claims 1-5, characterized in that, The first cylinder is provided with a first air intake port that communicates with the upper cavity; The second cylinder is provided with a second air intake port that communicates with the lower cavity; The partition is disposed between the first cylinder and the second cylinder, forming an air storage chamber; The air storage chamber has an air inlet, a first air outlet, and a second air outlet communicating with the air storage chamber; the first air outlet and the second air outlet are arranged opposite to each other on both sides of the air storage chamber, and correspondingly the first air intake and the second air intake are located on both sides of the axis of the dual rotor pump body assembly. The first air outlet and the first air inlet are connected; the second air outlet and the second air inlet are connected. External gas enters the gas storage chamber through the air inlet. The gas in the gas storage chamber enters the upper cavity through the first air outlet and the first air intake, and enters the lower cavity through the second air outlet and the second air intake.

8. A twin-rotor compressor, characterized in that, It includes a distributor and a dual rotor pump body assembly as described in any one of claims 1-7.

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