Symmetrical single-claw rotor and claw type fluid machine with same

Abstract

The invention relates to the field of variable-capacity fluid machinery, in particular to a symmetrical single-claw rotor and claw-type fluid machinery with the single-claw rotors, and the symmetrical single-claw rotor comprises two claw-type rotors which have the same section molded line and can do synchronous different-direction double-rotation motion around respective rotation centers; the section molded line of the claw type rotor comprises a cycloid, a point, a claw top arc, an eccentric arc, a high-order curve, a pitch circle arc, a conjugate curve of the high-order curve, a conjugate curve of the eccentric arc and a claw bottom arc which are connected in sequence. According to the invention, the section molded lines of the two claw rotors are completely the same, and the claw parts of the claw rotors are composed of the cycloids, the claw top arcs, the eccentric arcs and the high-order curves, so that the formation of a plurality of working cavities in the mixing process is avoided, and the problem of multiple compression and expansion of gas caused by the segmentation and combination of the plurality of working cavities in the mixing process is solved; irreversible loss and power consumption are reduced, and the working efficiency can be effectively improved.

Description

Technical Field

[0001] This invention relates to the field of variable displacement fluid machinery, and more specifically to a symmetrical single-claw rotor and a claw-type fluid machinery having the single-claw rotor. Background Technology

[0002] Claw-type fluid machinery mainly consists of a cylinder, end caps, a pair of meshing claw rotors, an intake port, and an exhaust port. During operation, the two claw rotors rotate synchronously and in opposite directions around their respective centers of rotation. Multiple working chambers are formed between the two rotors, and the volume of each chamber changes periodically with the rotation angle, thus completing the pressurization and delivery of the gas. Claw-type fluid machinery offers advantages such as internal compression, dry oil-free operation, compact structure, easy connection in series, and high reliability, and is widely used in semiconductor manufacturing, aerospace, photovoltaic integration, and petrochemical industries.

[0003] The claw rotor is a key component of claw fluid machinery. Optimizing the rotor cross-sectional profile is one of the key factors in improving the efficiency of claw fluid machinery and reducing power consumption and leakage.

[0004] Due to the unique structural characteristics of claw rotors, claw fluid machinery undergoes a unique and complex mixing process in addition to the intake, compression, and exhaust processes during operation, resulting in low working efficiency and high power consumption. Summary of the Invention

[0005] In view of this, the present invention provides a symmetrical single-claw rotor and a claw-type fluid machine having the single-claw rotor, aiming to improve working efficiency and reduce power consumption.

[0006] To solve the above technical problems, the technical solution adopted by the present invention is as follows: A symmetrical single-claw rotor includes two claw rotors with the same cross-sectional profile that can perform synchronous and opposite-directional double-rotation motion around their respective rotation centers; the cross-sectional profile of the claw rotor includes a cycloid, a point, a claw top arc, an eccentric arc, a higher-order curve, a pitch circle arc, a conjugate curve of the higher-order curve, a conjugate curve of the eccentric arc, and a claw bottom arc connected in sequence.

[0007] As an optional implementation, a rectangular coordinate system is established with the rotation center of the claw rotor as the origin, and a coordinate system with radius [missing information]. R The claw tip circle of 1 has a radius of 1. R The pitch circle and radius of 2 are R The radius of the claw base circle is 3. R Use the eccentric circle of 4 as a reference; The shape of the cycloid is determined by the following equation:

[0008] in,x AB ( t ), y AB ( t ) for cycloid x , y The corresponding coordinates on the axis; t For angle parameters; The shape of the claw tip arc is determined by the following equation:

[0009] in, x BC ( t ), y BC ( t ( ) is the claw tip arc in x , y The corresponding coordinates on the axis; The shape of the eccentric circular arc is determined by the following equation:

[0010] in, x CD ( t ), y CD ( t ) is an eccentric circular arc in x , y The corresponding coordinates on the axis; α The central angle of the claw tip arc; The shape of the higher-order curve is determined by the following equation:

[0011] in, x DE ( t ), y DE ( t ) is a higher-order curve in x , y The corresponding coordinates on the axis; a 0、 a 1. a 2. a 3 represents the coefficients of higher-order curves, determined by the following system of equations:

[0012] in, β The central angle of the eccentric arc. θ The central angle of a higher-order curve; The shape of the pitch circle arc is determined by the following equation:

[0013] in, x EF ( t ), y EF ( t ) is the arc of the pitch circle in x , y The corresponding coordinates on the axis; The shape of the conjugate curve of the higher-order curve is determined by the following equation:

[0014] in, x FG ( t ), y FG ( t () is the conjugate curve of a higher-order curve. x , y The corresponding coordinates on the axis; φ 1 represents the positional parameter of the conjugate curve of the higher-order curve, determined by the following equation:

[0015] in, f ( t, φ 1) The equation of the envelope of a higher-order curve obtained by the envelope method; The shape of the conjugate curve of the eccentric circular arc is determined by the following equation:

[0016] in, x GH ( t ), y GH ( t () is the conjugate curve of an eccentric circular arc in x , y The corresponding coordinates on the axis; φ 2 represents the positional parameter of the conjugate curve of the eccentric circular arc, determined by the following equation:

[0017] in, f ( t, φ 2) The equation of the envelope of the eccentric circular arc is obtained by using the envelope method; The shape of the arc at the bottom of the claw is determined by the following equation:

[0018] in, x HA ( t ), y HA ( t (The claw bottom arc is in) x , y The corresponding coordinates on the axis.

[0019] A claw-type fluid machine includes two claw-type rotors as described above. The two claw-type rotors perform synchronous and opposite-directional double-rotation motions around their respective rotation centers. The distance between the rotation centers of the two claw-type rotors is the diameter of the pitch circle. During the synchronous and opposite-directional double-rotation motion of the two claw-type rotors, the cycloid, point, claw top arc, eccentric arc, higher-order curve, pitch circle arc, conjugate curve of higher-order curve, conjugate curve of eccentric arc, and claw bottom arc of one claw-type rotor respectively mesh with the point, cycloid, claw bottom arc, conjugate curve of eccentric arc, conjugate curve of higher-order curve, pitch circle arc, higher-order curve, eccentric arc, and claw top arc of the other claw-type rotor.

[0020] As an optional implementation, it further includes a cylinder, a front cover, a rear cover, an intake port, and an exhaust port; the cylinder has a pump chamber that accommodates two claw rotors; the front cover and the rear cover are respectively encapsulated at both ends of the cylinder; when the two claw rotors perform synchronous and opposite double-rotation motion, they divide the pump chamber into two working chambers; the two working chambers are used for intake, mixing, compression, and exhaust respectively; the intake port is located on at least one of the front cover and the rear cover; the exhaust port is located on at least one of the front cover and the rear cover; the intake port and the exhaust port are respectively provided for the two claw rotors.

[0021] As an optional implementation, the cross-sectional profile of the pump cavity includes two connected circular arcs; the radii of the two circular arcs are the same and slightly larger than the radius of the claw top circle, and the center distance between the two circular arcs is the diameter of the pitch circle.

[0022] As an optional implementation, a rectangular coordinate system is established with the rotation center of one of the claw rotors as the origin, and the shapes of the two circular arcs of the pump cavity are determined by the following equations:

[0023]

[0024] in, x MNO ( t ), y MNO ( t ) is one segment of an arc in x ,y The corresponding coordinates on the axis x OPM ( t ), y OPM ( t ( ) is another arc in x , y The corresponding coordinates on the axis; R 9 represents the radius corresponding to the arc of the pump cavity.

[0025] As an optional implementation, the air intake is arc-shaped; the starting position of the air intake is determined by the cycloid of the claw rotor corresponding to the end of the mixing process; the ending position of the air intake is determined by the conjugate curve of the higher-order curve of the claw rotor corresponding to the start of the mixing process.

[0026] As an optional implementation, the cross-sectional profile of the air intake includes a second inner arc, a second end arc one, a second outer arc, and a second end arc two connected in sequence. Establish a rectangular coordinate system with the rotation center of one of the claw rotors as the origin, and plot the coordinates with radii of... R The pitch circle and radius of 2 are R Use the claw bottom circle of number 3 as a reference; The shape of the second inner arc is determined by the following equation:

[0027] in, x kl ( t ), y kl ( t () is the second inner arc in x , y The corresponding coordinates on the axis; R 5 is the radius corresponding to the second inner arc, and R 5 ＞R 3; The shape of the second outer arc is determined by the following equation:

[0028] in, x ij ( t ), y ij ( t () is the second outer arc in x , y The corresponding coordinates on the axis; R 6 is the radius corresponding to the second outer arc. R 6= R 5+l 1, l 1 represents the radial distance between the second inner arc and the second outer arc, and R 5< R 6< R 2.

[0029] As an optional implementation, the exhaust port is arc-shaped; the starting position of the exhaust port is determined by the pressure ratio, content ratio and intake volume of the claw fluid machinery, and is constrained by the conjugate curve of the higher-order curve of the corresponding claw rotor; the ending position of the exhaust port is determined by the cycloid of the claw rotor at the start of the mixing process.

[0030] As an optional implementation, the cross-sectional profile of the exhaust port includes a first inner arc, a first end arc one, a first outer arc, and a first end arc two connected in sequence. Establish a rectangular coordinate system with the rotation center of one of the claw rotors as the origin, and plot the coordinates with radii of... R The pitch circle and radius of 2 are R Use the claw bottom circle of number 3 as a reference; The shape of the first inner arc is determined by the following equation:

[0031] in, x IJ ( t ), y IJ ( t () is the first inner arc in x , y The corresponding coordinates on the axis; R 7 is the radius corresponding to the first inner arc, and R 7 ＞R 3; The shape of the first outer arc is determined by the following equation:

[0032] in, x KL ( t ), y KL ( t ) is the first outer arc in x , y The corresponding coordinates on the axis; R 8 represents the radius corresponding to the first outer arc. R 8= R 7+ l 2, l 2 is the radial distance between the first inner arc and the first outer arc, andR 7< R 8< R 2.

[0033] In summary, compared with the prior art, the present invention has the following advantages and beneficial effects: In the present invention, since the cross-sectional profiles of the two claw rotors are exactly the same, and the claw part of the claw rotor is composed of cycloid, claw top arc, eccentric arc and higher order curve, the formation of multiple working chambers during the mixing process is avoided, the problem of gas compression and expansion caused by the division and merging of multiple working chambers during the mixing process is solved, irreversible losses and power consumption are reduced, and the working efficiency can be effectively improved. Attached Figure Description

[0034] Figure 1 This is a schematic diagram of the cross-sectional profile of a symmetrical single-claw rotor as described in Embodiment 1 of the present invention.

[0035] Figure 2 This is a schematic cross-sectional profile of the first claw rotor described in Embodiment 1 of the present invention.

[0036] Figure 3 This is a schematic cross-sectional profile of the second claw rotor described in Embodiment 1 of the present invention.

[0037] Figure 4 This is an exploded structural diagram of the claw-type fluid machinery described in Embodiment 2 of the present invention.

[0038] Figure 5 This is a schematic diagram of the cross-sectional profile of the pump cavity as described in Embodiment 2 of the present invention.

[0039] Figure 6 This is a schematic diagram showing the positional relationship between the cross-sectional profile of the air intake and the first claw rotor and the second claw rotor as described in Embodiment 2 of the present invention.

[0040] Figure 7 This is a schematic diagram showing the positional relationship between the cross-sectional profile of the exhaust port and the first claw rotor and the second claw rotor as described in Embodiment 2 of the present invention.

[0041] Figures 8-12 This mainly illustrates the state relationship between the first claw rotor, the second claw rotor, and the pump chamber during the air intake process of the claw fluid machinery described in Embodiment 2 of the present invention.

[0042] Figures 12-19 This mainly illustrates the state relationship between the first claw rotor, the second claw rotor, and the pump chamber during the first mixing process of the claw fluid machinery described in Embodiment 2 of the present invention.

[0043] Figures 19-22This mainly illustrates the state relationship between the first claw rotor, the second claw rotor, and the pump chamber during the compression process of the claw fluid machinery described in Embodiment 2 of the present invention.

[0044] Figures 22-26 This mainly illustrates the state relationship between the first claw rotor, the second claw rotor, and the pump chamber during the exhaust process of the claw fluid machinery described in Embodiment 2 of the present invention.

[0045] Figures 26-33 This mainly illustrates the state relationship between the first claw rotor, the second claw rotor, and the pump chamber in the second mixing process of the claw fluid machinery described in Embodiment 2 of the present invention.

[0046] The definitions of the reference numerals in the attached figures are as follows: 1. Front end cover; 2. First claw rotor; 3. First cycloid. AB First point B The first claw tip arc BC (The corresponding radius is) R 1), α The first claw tip arc BC The central angle, the first eccentric arc CD (The corresponding radius is) R 4) β For the first eccentric arc CD Central angle, first higher order curve DE , θ The first higher order curve DE The central angle, the first arc of the circle EF (The corresponding radius is) R 2) Conjugate curves of the first higher-order curve FG The conjugate curve of the first eccentric circular arc GH The first claw bottom arc HA (The corresponding radius is) R 3), Second claw rotor 3, Second cycloid ab Second point b The second claw tip arc bc Second eccentric arc cd Second higher order curve de The second section is a circular arc. ef The conjugate curve of the second higher-order curve fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Cylinder 4, First Arc MNO (The corresponding radius is) R 9), Second arc OPM (The corresponding radius is) R9) Intake chamber 401, first mixing chamber 402, compression chamber 403, exhaust chamber 404, second mixing chamber 405, rear end cover 5, intake port 501, second inner arc kl (The corresponding radius is) R 5) The second end arc li Second outer arc ij (The corresponding radius is) R 6) Second end arc jk Exhaust port 502, first inner arc IJ (The corresponding radius is) R 7) First end arc JK First outer arc KL (The corresponding radius is) R 8), First end arc two LI . Detailed Implementation

[0047] To enable those skilled in the art to better understand the technical solution of the present invention, the present invention will be further described in detail below with reference to specific embodiments.

[0048] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0049] In the description of this invention, "several" means one or more, "multiple" means two or more, "greater than," "less than," "exceeding," etc. are understood to exclude the stated number, while "above," "below," "within," etc. are understood to include the stated number. If terms such as "first," "second," etc., are used only to distinguish technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0050] In the description of this invention, unless otherwise explicitly defined, terms such as "set up," "install," and "connect" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this invention in conjunction with the specific content of the technical solution.

[0051] Example 1 The applicant discovered that after the exhaust process of the working chamber of the claw-type fluid machinery, unexhausted compressed gas remains in the working chamber. This volume of the working chamber after the exhaust process is generally referred to as the clearance volume. The unexhausted compressed gas remaining in the clearance volume mixes with the gas drawn in after the intake process of other working chambers, and then re-enters the compression process.

[0052] For example, Chinese patent CN108757464B discloses a straight claw rotor for a claw vacuum pump and its profile design method, as shown in its appendix. Figure 3 As shown, the two claw rotors divide the pump chamber into three working chambers. Two of these working chambers undergo splitting and merging during the mixing process, ultimately forming the structure shown above. Figure 6 The diagram shows one working chamber. The applicant discovered that during the mixing process, multiple working chambers are divided and merged, and the volume of the working chambers undergoes complex evolution. The gas inside the working chambers undergoes multiple complex irreversible thermodynamic processes such as compression, expansion, and mixing, resulting in low working efficiency and high power consumption of the claw-type fluid machinery.

[0053] The reasons are as follows: First, after the exhaust process, the clearance volume formed between the claw rotors is relatively large, and there is a lot of residual compressed gas. As the rotors rotate, the clearance volume decreases, leading to overcompression of the gas in the clearance volume and increased power consumption. Second, during the mixing process, multiple working chambers are formed between the two claw rotors. These working chambers are divided and merged, causing the gas in the working chambers to undergo multiple complex irreversible thermodynamic processes such as compression, expansion and mixing, resulting in irreversible losses and energy dissipation. Third, during the mixing process, the compressed gas in the clearance volume flows to another working chamber through the meshing gap between the rotors. The gas flow field in the working chamber changes transiently, causing flow losses and reducing the working efficiency of the claw fluid machinery.

[0054] Based on the above findings, this invention introduces a symmetrical single-claw rotor, such as... Figure 1 As shown, it includes two claw rotors with identical cross-sectional profiles that can perform synchronous, opposite-directional double-rotational motions around their respective rotation centers. The cross-sectional profile of the claw rotor is mainly a continuous curve composed of 8 segments. Specifically, it is a continuous curve composed of 1 cycloid segment, 3 circular arc segments, 1 eccentric circular arc segment, 1 higher-order curve segment, 1 conjugate curve of the eccentric circular arc segment, 1 conjugate curve of the higher-order curve segment, and 1 point. The point is the common endpoint of the adjacent cycloid segment and circular arc segment and serves as the tip of the claw of the claw rotor. Except for the tip of the claw, the rest of the continuous curve is smoothly connected.

[0055] For ease of description, one of the claw rotors is referred to as the first claw rotor 2, and it is assumed that the first claw rotor 2 rotates clockwise, while the other is referred to as the second claw rotor 3, and it is assumed that the second claw rotor 3 rotates counterclockwise.

[0056] like Figure 2 As shown, the cross-sectional profile of the first claw rotor 2 includes the profile in the opposite direction to the rotation direction (i.e., Figure 1 The first cycloid (connected sequentially in a counter-clockwise direction) AB First point B The first claw tip arc BC First eccentric arc CD First higher order curve DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG The conjugate curve of the first eccentric circular arc GH The first claw bottom arc HA .

[0057] The design method for the first claw rotor 2 is as follows: (1) such as Figure 2 As shown, with the rotation center of the first claw rotor 2 O 1. Establish a rectangular coordinate system with the origin, and draw the coordinates with radius as follows: R The claw tip circle of 1 has a radius of 1. R The pitch circle and radius of 2 are R The radius of the claw base circle is 3. R Use the eccentric circle of 4 as a reference.

[0058] (2) The first cycloid AB The shape of the line is determined by the following equation:

[0059] in, x AB ( t ), y AB ( t () is the first cycloid AB exist x , y The corresponding coordinates on the axis t For angle parameters.

[0060] (3) The first claw tip arc BC The shape of the line is determined by the following equation:

[0061] in, x BC ( t ), y BC ( t ( ) is the arc of the first claw tip. BC exist x , y The corresponding coordinates on the axis.

[0062] (4) The first eccentric arc CD The shape of the line is determined by the following equation:

[0063] in, x CD ( t ), y CD ( t () is the first eccentric arc CD exist x , y The corresponding coordinates on the axis α The first claw tip arc BC The central angle.

[0064] (5) The first higher-order curve DE The shape of the line is determined by the following equation:

[0065] in, x DE ( t ), y DE ( t () is the first higher order curve DE exist x , y The corresponding coordinates on the axis.

[0066] a 0、 a 1. a 2. a 3 is the first higher order curve DE The coefficients of are determined by the following system of equations:

[0067] in, β For the first eccentric arc CD The central angle; θ The first higher order curve DE The central angle.

[0068] (6) The first section of the circular arc EF The shape of the line is determined by the following equation:

[0069] in, x EF ( t ), y EF ( t () is the first section of the circular arc EFexist x , y The corresponding coordinates on the axis.

[0070] (7) The conjugate curve of the first higher-order curve FG The shape of the line is determined by the following equation:

[0071] in, x FG ( t ), y FG ( t () is the conjugate curve of the first higher-order curve. FG exist x , y The corresponding coordinates on the axis.

[0072] φ 1 is the conjugate curve of the first higher-order curve. FG The position parameters are determined by the following equations:

[0073] in, f ( t, φ 1) The first higher-order curve obtained using the envelope method. DE The envelope equation.

[0074] (8) The conjugate curve of the first eccentric circular arc GH The shape of the line is determined by the following equation:

[0075] in, x GH ( t ), y GH ( t () is the conjugate curve of the first eccentric circular arc. GH exist x , y The corresponding coordinates on the axis.

[0076] φ 2 is the conjugate curve of the first eccentric circular arc. GH The position parameters are determined by the following equations:

[0077] in, f ( t, φ 2) The first eccentric circular arc is solved using the envelope method. CD The envelope equation.

[0078] (9) The bottom arc of the first claw HA The shape of the line is determined by the following equation:

[0079] in, x HA ( t ), y HA ( t ( ) is the arc of the bottom of the first claw. HA exist x , y The corresponding coordinates on the axis.

[0080] like Figure 3 As shown, the cross-sectional profile of the second claw rotor 3 includes the profiles arranged in the direction of rotation (i.e., Figure 1 The second cycloid (connected sequentially in a counter-clockwise direction) ab Second point b The second claw tip arc bc Second eccentric arc cd Second higher order curve de Section 2 Circular Arc ef Conjugate curves of the second higher order curve fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha .

[0081] The design method of the second claw rotor 3 is the same as that of the first claw rotor 2, and will not be repeated here.

[0082] Based on the radius R The pitch circle of rotor 2 determines the relative position between the second claw rotor 3 and the first claw rotor 2. Specifically, it determines the rotation center of the second claw rotor 3. O 2 and the rotation center of the first claw rotor 2 O The distance between 1 is the diameter of the pitch circle, i.e., 2. R 2. The cross-sectional profile of the second claw rotor 3 is exactly the same as that of the first claw rotor 2. The cross-sectional profile of the second claw rotor 3 can be obtained by rotating the cross-sectional profile of the first claw rotor 2.

[0083] When the first claw rotor 2 and the second claw rotor 3 perform synchronous and opposite-directional double-rotation motion, the cross-sectional profiles of the first claw rotor 2 and the second claw rotor 3 can achieve correct meshing. The meshing relationship is as follows: the first cycloid of the first claw rotor 2 AB First point B The first claw tip arc BC First eccentric arc CD First higher order curve DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG The conjugate curve of the first eccentric circular arc GH The first claw bottom arc HA The second point of the second claw rotor 3 respectively b Second cycloid ab The second claw bottom arc ha The conjugate curve of the second eccentric circular arc gh Conjugate curves of the second higher order curve fg Section 2 Circular Arc ef Second higher order curve de Second eccentric arc cd The second claw tip arc bc Engage.

[0084] In this invention, the claw rotors (2; 3) employ eccentric circular arcs ( CD ; cd ) and higher-order curves ( DE ; de Connecting claw top arc ( BC ; bc ) and pitch circle arc ( EF ; ef ), using the conjugate curve of a higher-order curve ( FG ; fg ) and the conjugate curve of the eccentric circular arc ( GH ; gh Connecting nodal arc ( EF ; ef ) and claw bottom arc ( HA ; ha This reduces the rough connection points of the claw rotor (2;3), improves the mechanical properties of the claw rotor (2;3) such as wear, deformation and stress concentration, and makes the cross-sectional profile of the claw rotor (2;3) simple, easy to process and low in processing cost.

[0085] Comparative verification shows that the symmetrical single-claw rotor introduced in this invention can effectively improve working efficiency and reduce power consumption.

[0086] Example 2 like Figure 4 As shown, the present invention also introduces a claw-type fluid machinery, including a cylinder 4, a front end cover 1, a rear end cover 5, an intake port 501, an exhaust port 502, and a first claw-type rotor 2 and a second claw-type rotor 3 as described in Embodiment 1.

[0087] The cylinder 4 is generally annular, with an internal pump chamber that accommodates the first claw rotor 2 and the second claw rotor 3, and the front and rear ends are open.

[0088] like Figure 5 As shown, the cross-sectional profile of the pump cavity includes two connected circular arcs, namely the first circular arc. MNO Second arc OPM First arc MNO Second arc OPM The radii are all R 9, and R 9 is slightly larger than the radius of the claw tip circle. R 1. For example, when R When 1 = 50 mm, R The value of 9 ranges from 50.04 mm to 50.08 mm. First arc. MNO Second arc OPM The center-to-center distance is the diameter of the pitch circle, which is 2. R 2.

[0089] The design method for the pump chamber is as follows: (1) such as Figure 5 As shown, with the rotation center of the first claw rotor 2 O Establish a rectangular coordinate system with the origin as the origin.

[0090] (2) First arc MNO The shape of the line is determined by the following equation:

[0091] in, x MNO ( t ), y MNO ( t () is the first arc MNO exist x , y The corresponding coordinates on the axis.

[0092] (3) Second arc OPM The shape of the line is determined by the following equation:

[0093] in, x OPM ( t ), y OPM ( t () is the second arc OPM exist x , y The corresponding coordinates on the axis.

[0094] The front cover 1 and the rear cover 5 are respectively encapsulated at both ends of the cylinder 4. The front cover 1, the rear cover 5, and the cylinder 4 enclose the pump chamber, so that when the first claw rotor 2 and the second claw rotor 3 perform synchronous and opposite-directional double-rotation motion in the pump chamber, the pump chamber is divided into two relatively independent working chambers, which are used for intake, mixing, compression, and exhaust respectively. Because the claw rotors (2; 3) adopt an eccentric circular arc ( CD ; cd This increases the length of the leakage channel between the claw rotor (2; 3) and the pump cavity wall, effectively reducing gas leakage between the claw rotor (2; 3) and the pump cavity wall.

[0095] During operation, gas enters cylinder 4 through intake port 501. A periodically changing working chamber is formed between the front cover 1, the first claw rotor 2, the second claw rotor 3, cylinder 4, and rear cover 5: intake chamber 401, first mixing chamber 402, compression chamber 403, exhaust chamber 404, and second mixing chamber 405, respectively completing the gas intake, first mixing, compression, exhaust, and second mixing processes. Gas is discharged from cylinder 4 through exhaust port 502.

[0096] The air intake 501 is located on at least one of the front end cover 1 and the rear end cover 5, and at a position corresponding to the first claw rotor 2 or the second claw rotor 3. For example, as Figure 4 and Figure 6 As shown, the air intake 501 can be set at the position corresponding to the second claw rotor 3 on the rear end cover 5 to prevent gas in the clearance volume of the claw fluid machinery from leaking out from the air intake 501 during operation.

[0097] The intake port 501 is preferably arc-shaped. To ensure maximum intake volume, the starting position of the intake port 501 is determined by the second cycloid of the second claw rotor 3 at the end of the mixing process (including the first and second mixing). ab The end position of the intake port 501 is determined by the conjugate curve of the second higher-order curve of the second claw rotor 3 at the start time of the mixing process (including the first and second mixing). fg Decide.

[0098] Optionally, the cross-sectional profile of the intake port 501 includes the direction of rotation along the second claw rotor 3 (i.e., Figure 6 The second inner arc (in a counter-clockwise direction) is connected sequentially. kl The second end arc li Second outer arc ij The second end arc jk Or, in other words, the cross-sectional profile of the intake port 501 is formed by the second inner arc. kl It is formed by offsetting a certain distance radially outward.

[0099] The design method of the air intake 501 is as follows: (1) With the rotation center of the first claw rotor 2 O 1. Establish a rectangular coordinate system with the origin as the origin, and plot the radius as... R The pitch circle and radius of 2 are R Use the claw bottom circle of number 3 as a reference.

[0100] (2) The second inner arc kl The shape of the line is determined by the following equation:

[0101] in, x kl ( t ), y kl ( t () is the second inner arc kl exist x , y The corresponding coordinates on the axis R 5 represents the second inner arc. kl The corresponding radius, and R 5> R 3.

[0102] (3) The second outer arc ij The shape of the line is determined by the following equation:

[0103] in, x ij ( t ), y ij ( t () is the second outer arc ij exist x , y The corresponding coordinates on the axis R 6 is the second outer arc ij The corresponding radius, R 6= R 5+ l 1, l 1 represents the second inner arc. kl The distance offset radially outward, i.e. l 1 represents the second inner arc. kl With the second outer arc ij The radial distance between them, and R 5< R 6< R 2.

[0104] (4) The second end arc li Second end arc jk It is the second inner arckl Second outer arc ij The transitional arc at the end adapts to changes in its linear shape.

[0105] The exhaust port 502 is located on at least one of the front end cover 1 and the rear end cover 5, and at a position corresponding to the first claw rotor 2 or the second claw rotor 3. For example, as Figure 4 and Figure 7 As shown, the exhaust port 502 can be set at the position corresponding to the first claw rotor 2 on the rear end cover 5 to prevent gas from leaking out of the exhaust port 502 during the intake process, compression process and mixing process (including the first mixing and the second mixing) of the claw fluid machinery, which would result in the inability to meet the pressure ratio requirements.

[0106] The exhaust port 502 is preferably arc-shaped. The starting position of the exhaust port 502 is determined by the pressure ratio, internal ratio, and intake volume of the claw-type fluid machinery, and is also influenced by the conjugate curve of the first higher-order curve of the first claw rotor 2. FG Constraints. To ensure maximum exhaust volume and prevent the intake chamber 401 from communicating with the exhaust port 502, the end position of the exhaust port 502 is determined by the first cycloid of the first claw rotor 2 at the start of the mixing process (including the first and second mixing). AB Decide.

[0107] Optionally, the cross-sectional profile of the exhaust port 502 includes the opposite direction to the rotation direction of the first claw rotor 2 (i.e., Figure 7 The first inner arc (connected sequentially in a counter-clockwise direction) IJ The first end arc JK First outer arc KL First end arc two LI Or, in other words, the cross-sectional profile of the exhaust port 502 is formed by the first inner arc. IJ It is formed by offsetting a certain distance radially outward.

[0108] The design method for exhaust port 502 is as follows: (1) With the rotation center of the first claw rotor 2 O 1. Establish a rectangular coordinate system with the origin as the origin, and plot the radius as... R The pitch circle and radius of 2 are R Use the claw bottom circle of number 3 as a reference.

[0109] (2) The first inner arc IJ The shape of the line is determined by the following equation:

[0110] in, x IJ ( t ), yIJ ( t () is the first inner arc IJ exist x , y The corresponding coordinates on the axis R 7 represents the first inner arc. IJ The corresponding radius, and R 7 ＞R 3.

[0111] (3) The shape of the first outer arc is determined by the following equation:

[0112] in, x KL ( t ), y KL ( t () is the first outer arc KL exist x , y The corresponding coordinates on the axis R 8 represents the first outer arc. KL The corresponding radius, R 8= R 7+ l 2, l 2 represents the first inner arc. IJ The distance offset radially outward, i.e. l 2 represents the first inner arc. IJ With the first outer arc KL The radial distance between them, and R 7< R 8< R 2.

[0113] (4) The first end arc JK And the first end arc two LI It is connected to the first inner arc. IJ and the first outer arc KL The transitional arc at the end adapts to changes in its linear shape.

[0114] The suction process of claw-type fluid machinery is as follows Figures 8-12 As shown.

[0115] The initial moment of the inhalation process, such as Figure 8 As shown. At the initial moment of the intake process, the first higher-order curve of the first claw rotor 2. DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0116] In the two relatively independent working chambers separated by the first claw rotor 2 and the second claw rotor 3, the first claw tip arc of the first claw rotor 2... BC First eccentric arc CD First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid ab The working cavity formed by the front cover 1 and the rear cover 5 serves as the air intake cavity 401. At this time, the air intake cavity 401 is about to be connected to the air intake port 501.

[0117] During the intake process, the intake chamber 401 is connected to the intake port 501, but the intake chamber 401 is never connected to the exhaust port 502. Gas enters the intake chamber 401 from the intake port 501. The first higher-order curve of the first claw rotor 2. DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG Conjugate curves with the second higher-order curves of the second claw rotor 3 fg Section 2 Circular Arc ef Second higher order curve de Engage in sequence, such as Figure 8 The first claw tip arc shown is formed by the first claw rotor 2. BC First eccentric arc CD First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid ab The air intake chamber 401, formed by the front cover 1 and the rear cover 5, gradually becomes like... Figure 12 The first eccentric arc shown is formed by the first claw rotor 2. CD First higher order curve DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Section 2 Circular Arc ef Conjugate curves of the second higher order curve fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid abThe intake chamber 401 is formed by the combination of the front cover 1, the rear cover 5 and the inner wall of the cylinder 4 pump chamber, and the volume of the intake chamber 401 gradually increases, drawing in gas from the intake port 501.

[0118] The end of the inhalation process, such as Figure 12 As shown. At the end of the intake process, the conjugate curve of the first higher-order curve of the first claw rotor 2. FG The second higher order curve of the second claw rotor 3 de Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0119] The intake chamber 401 is formed by the first eccentric arc of the first claw rotor 2. CD First higher order curve DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Section 2 Circular Arc ef Conjugate curves of the second higher order curve fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid ab The front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber are combined to form a suction chamber 401 that is separated from the suction port 501.

[0120] When the intake process ends, the first mixing process begins, and the intake chamber 401 transforms into the first mixing chamber 402. The first mixing process of the claw-type fluid machinery is as follows: Figures 12-19 As shown.

[0121] The initial moment of the first mixing process is as follows: Figure 12 As shown. The first mixing chamber 402 is still composed of the first eccentric arc of the first claw rotor 2. CD First higher order curve DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Section 2 Circular Arc ef Conjugate curves of the second higher order curve fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid ab It is formed by combining the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber.

[0122] During the mixing process, the first mixing chamber 402 is not connected to either the intake port 501 or the exhaust port 502. The conjugate curve of the first higher-order curve of the first claw rotor 2. FG The conjugate curve of the first eccentric circular arc GH The first claw bottom arc HA First cycloid AB First point B The first claw tip arc BC First eccentric arc CD First higher order curve DE The second higher order curves of the second claw rotor 3 are respectively compared with those of the second claw rotor 3. de Second eccentric arc cd The second claw tip arc bc Second point b Second cycloid ab The second claw bottom arc ha The conjugate curve of the second eccentric circular arc gh Conjugate curves of the second higher order curve fg Engage.

[0123] Specifically, such as Figure 12 As shown, the conjugate curve of the first higher-order curve of the first claw rotor 2 FG The second higher order curve of the second claw rotor 3 de Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0124] like Figure 13 As shown, the conjugate curve of the first higher-order curve of the first claw rotor 2 FG The second higher order curve of the second claw rotor 3 de Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0125] like Figure 14 As shown, the conjugate curve of the first eccentric circular arc of the first claw rotor 2 GH With the second eccentric arc of the second claw rotor 3 cd Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0126] like Figure 15 As shown, the first claw bottom arc of the first claw rotor 2 HA The second claw tip arc of the second claw rotor 3 bc Engagement, and the first cycloid of the first claw rotor 2 ABThe second point of the second claw rotor 3 b Meshing.

[0127] like Figure 16 As shown, the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0128] like Figure 17 As shown, the first claw tip arc of the first claw rotor 2 BC The second claw bottom arc of the second claw rotor 3 ha Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0129] like Figure 18 As shown, the first eccentric arc of the first claw rotor 2 CD Conjugate curve of the second eccentric circular arc of the second claw rotor 3 gh Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0130] like Figure 19 As shown, the first higher-order curve of the first claw rotor 2 DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0131] In the first mixing process, such as Figure 12 The first eccentric arc shown is formed by the first claw rotor 2. CD First higher order curve DE Section 1: Circular Arc EF Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Section 2 Circular Arc ef Conjugate curves of the second higher order curve fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid ab The first mixing chamber 402, formed by the combination of the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber, gradually transforms into... Figure 19 The first cycloid shown is formed by the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Section 2 Circular Arc ef Second higher order curve de Second eccentric arc cd The first mixing chamber 402, formed by the combination of the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber, first increases in volume ( Figures 12-15 ), then reduce ( Figures 15-16 ), and increase again ( Figures 16-17 ), decrease again ( Figures 17-19 The dynamic evolution process of ).

[0132] The end time of the first mixing process is as follows Figure 19 As shown. At the end of the first mixing process, the first higher-order curve of the first claw rotor 2. DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0133] The first mixing chamber 402 is still controlled by the first cycloid of the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Section 2 Circular Arc ef Second higher order curve de Second eccentric arc cd It is formed by combining the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber.

[0134] During the first mixing process, the gas remaining in the other working chamber will leak into the first mixing chamber 402 through the meshing gap between the rotors and mix with the gas in the first mixing chamber 402. The gas flow fields in the first mixing chamber 402 and the other working chamber undergo complex mixing until dynamic equilibrium is reached.

[0135] When the first mixing process ends, the compression process begins, and the first mixing chamber 402 transforms into the compression chamber 403. The compression process of the claw-type fluid machinery is as follows: Figures 19-22 As shown.

[0136] The initial moment of the compression process, such as Figure 19 As shown. The compression chamber 403 is still composed of the first cycloid of the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Section 2 Circular Arc ef Second higher order curve de Second eccentric arc cd It is formed by combining the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber.

[0137] During compression, neither the intake port 501 nor the exhaust port 502 is connected to the compression chamber 403. The first higher-order curve of the first claw rotor 2. DE Section 1: Circular Arc EF Conjugate curves with the second higher-order curves of the second claw rotor 3 fg Section 2 Circular Arc ef Engagement, such as Figure 19 The first cycloid shown is formed by the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg、 Section 2 Circular Arcs ef Second higher order curve de Second eccentric arc cd The compression chamber 403, formed by the combination of the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber, gradually transforms into... Figure 22 The first cycloid shown is formed by the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF With the second segment of the circular arc of the second claw rotor 3 ef Second higher order curve deSecond eccentric arc cd The compression chamber 403 is formed by the combination of the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber. The volume of the compression chamber 403 gradually decreases, and the pressure of the gas in the compression chamber 403 gradually increases.

[0138] The end time of the compression process, such as Figure 22 As shown. At the end of the compression process, the first segment of the first claw rotor 2... EF With the second segment of the circular arc of the second claw rotor 3 ef Meshing.

[0139] Compression chamber 403 is still composed of the first cycloid of the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF With the second segment of the circular arc of the second claw rotor 3 ef Second higher order curve de Second eccentric arc cd It is formed by combining the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber.

[0140] When the compression process ends, the exhaust process begins, and the compression chamber 403 transforms into the exhaust chamber 404. The exhaust process of the claw-type fluid machinery is as follows: Figures 22-26 As shown.

[0141] The initial moment of the exhaust process, such as Figure 22 As shown. The exhaust chamber 404 is still controlled by the first cycloid of the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF With the second segment of the circular arc of the second claw rotor 3 ef Second higher order curve de Second eccentric arc cd It is formed by combining the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber.

[0142] During the exhaust process, the exhaust chamber 404 is connected to the exhaust port 502, but the exhaust chamber 404 is never connected to the intake port 501. The gas in the exhaust chamber 404 is discharged from the exhaust port 502. The first segment of the first claw rotor 2 is a circular arc. EF Conjugate curve of the first higher-order curve FG The second circular arc of the second claw rotor 3 is respectively connected to the second section of the circular arc. ef、 Second higher order curve de Engagement, such as Figure 22The first cycloid shown is formed by the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG Section 1: Circular Arc EF With the second segment of the circular arc of the second claw rotor 3 ef Second higher order curve de Second eccentric arc cd The exhaust chamber 404, formed by the combination of the front cover 1, the rear cover 5, and the inner wall of the cylinder 4 pump chamber, gradually transforms into... Figure 26 The first cycloid shown is formed by the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Second eccentric arc cd The second claw tip arc bc The exhaust chamber 404 is formed by the front cover 1 and the rear cover 5, and the volume of the exhaust chamber 404 gradually decreases. The gas in the exhaust chamber 404 is discharged from the exhaust port 502.

[0143] The end time of the exhaust process is as follows Figure 26 As shown. At the end of the exhaust process, the conjugate curve of the first higher-order curve of the first claw rotor 2. FG The second higher order curve of the second claw rotor 3 de Meshing.

[0144] At this time, the exhaust chamber 404 is still controlled by the first cycloid of the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Second eccentric arc cd The second claw tip arc bc The front cover 1 and the rear cover 5 are combined to form the exhaust chamber 404. At this time, some compressed gas will remain in the exhaust chamber 404 and will not be discharged. The volume of the exhaust chamber 404 is the clearance volume.

[0145] When the exhaust process ends, the second mixing process begins, and the exhaust chamber 404 transforms into the second mixing chamber 405. The second mixing process of the claw-type fluid machinery is as follows: Figures 26-33 As shown.

[0146] The initial time of the second mixing process is as follows Figure 26 As shown. The second mixing chamber 405 is still composed of the first cycloid of the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FG The second higher order curve of the second claw rotor 3 de Second eccentric arc cd The second claw tip arc bc It is formed by combining the front cover 1 and the rear cover 5.

[0147] During the second mixing process, neither the intake port 501 nor the exhaust port 502 is connected to the second mixing chamber 405. The conjugate curve of the first higher-order curve of the first claw rotor 2. FG The conjugate curve of the first eccentric circular arc GH The first claw bottom arc HA First cycloid AB First point B The first claw tip arc BC First eccentric arc CD First higher order curve DE The second higher order curves of the second claw rotor 3 are respectively compared with those of the second claw rotor 3. de Second eccentric arc cd The second claw tip arc bc Second point b Second cycloid ab The second claw bottom arc ha The conjugate curve of the second eccentric circular arc gh Conjugate curves of the second higher order curve fg Engage.

[0148] Specifically, such as Figure 26 As shown, the conjugate curve of the first higher-order curve of the first claw rotor 2 FG The second higher order curve of the second claw rotor 3 de Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0149] like Figure 27 As shown, the conjugate curve of the first higher-order curve of the first claw rotor 2 FG The second higher order curve of the second claw rotor 3 de Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0150] like Figure 28 As shown, the conjugate curve of the first eccentric circular arc of the first claw rotor 2 GH With the second eccentric arc of the second claw rotor 3 cd Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0151] like Figure 29 As shown, the first claw bottom arc of the first claw rotor 2 HA The second claw tip arc of the second claw rotor 3 bc Engagement, and the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Meshing.

[0152] like Figure 30 As shown, the first cycloid of the first claw rotor 2 AB The second point of the second claw rotor 3 b Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0153] like Figure 31 As shown, the first claw tip arc of the first claw rotor 2 BC The second claw bottom arc of the second claw rotor 3 ha Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0154] like Figure 32 As shown, the first eccentric arc of the first claw rotor 2 CD Conjugate curve of the second eccentric circular arc of the second claw rotor 3 gh Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0155] like Figure 33 As shown, the first higher-order curve of the first claw rotor 2 DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0156] In the second mixing process, such as Figure 26 The first cycloid shown is formed by the first claw rotor 2. AB The first claw bottom arc HA The conjugate curve of the first eccentric circular arc GH Conjugate curves of the first higher-order curve FGThe second higher order curve of the second claw rotor 3 de Second eccentric arc cd The second claw tip arc bc The second mixing cavity 405, formed by the front cover 1 and the rear cover 5, gradually transforms into... Figure 33 The first claw tip arc shown is formed by the first claw rotor 2. BC First eccentric arc CD First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc ha Second cycloid ab The front cover 1 and the rear cover 5 are combined to form the second mixing chamber 405. The volume of the second mixing chamber 405 is first reduced to zero. Figures 26-30 ), and then a new instantaneous second mixing chamber 405 is formed again ( Figure 30 After the volume of the second mixing chamber 405 decreases to zero instantaneously ( Figures 30-31 A new second mixing chamber 405 is formed. Figure 31 The volume of the new second mixing chamber 405 gradually increases. Figures 31-33 Therefore, the volume of the second mixing chamber 405 has undergone a complex dynamic evolution process.

[0157] The residual gas in the second mixing chamber 405 will Figures 26-30 As the volume gradually decreases, the gas is compressed and leaks into another working chamber through the meshing gap between the rotors to mix with the gas in the other working chamber. The gas flow fields in the second mixing chamber 405 and the other working chamber undergo a complex mixing process until they reach dynamic equilibrium.

[0158] The end time of the second mixing process is as follows Figure 33 As shown. At the end of the second mixing process, the first higher-order curve of the first claw rotor 2. DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg Engagement, and the first point of the first claw rotor 2 B With the second cycloid of the second claw rotor 3 ab Meshing.

[0159] The second mixing chamber 405 is still composed of the first claw tip arc of the first claw rotor 2. BC First eccentric arc CD First higher order curve DE Conjugate curve of the second higher order curve of the second claw rotor 3 fg The conjugate curve of the second eccentric circular arc gh The second claw bottom arc haSecond cycloid ab It is formed by combining the front cover 1 and the rear cover 5.

[0160] In this invention, due to the use of the conjugate curve of a higher-order curve ( FG ; fg ) and the conjugate curve of the eccentric circular arc ( GH ; gh Connecting nodal arc ( EF ; ef ) and claw bottom arc ( HA ; ha This allows the two claw rotors (2;3) to mesh in a line-to-line manner when performing synchronous and opposite-direction double-rotation motion, effectively reducing gas leakage at the meshing gap between the claw rotors (2;3) and improving the volumetric efficiency of the claw fluid machinery.

[0161] This invention can be applied to, but is not limited to, claw vacuum pumps, claw hydrogen circulation pumps, and claw compressors.

[0162] Taking a claw vacuum pump as the research object, the flow rate and velocity field of the present invention applied to a claw vacuum pump and the claw vacuum pump disclosed in Chinese patent CN108757464B were analyzed using numerical simulation method. The volumetric efficiency of the two was obtained. It was found that the volumetric efficiency of the present invention applied to a claw vacuum pump was 3% to 5% higher than that of the claw vacuum pump disclosed in Chinese patent CN108757464B.

[0163] In this invention, since the cross-sectional profiles of the two claw rotors (2; 3) are exactly the same, both adopt cycloidal ( AB ; ab ), Claw tip arc ( BC ; bc ), eccentric arc ( CD ; cd ), higher order curve ( DE ; de The claw portion of the claw rotor (2; 3) avoids the formation of multiple working chambers in the first and second mixing processes, solves the problem of multiple compressions and expansions of gas caused by the division and merging of multiple working chambers in the mixing process, reduces irreversible losses and power consumption of the claw fluid machinery, and improves the efficiency of the claw fluid machinery.

[0164] Taking a claw vacuum pump as the research object, numerical simulation method was used to analyze the law of pressure field variation with working chamber volume when the present invention is applied to a claw vacuum pump and the claw vacuum pump disclosed in Chinese patent CN108757464B. The indicator diagrams of the two were obtained. It was found that when the present invention is applied to a claw vacuum pump, the power consumption is reduced by 8% to 15% compared with the claw vacuum pump disclosed in Chinese patent CN108757464B.

[0165] In this invention, the clearance volume is significantly reduced by adjusting the center angle of the claw tip arc. α The central angle of the eccentric arc β The radius of the eccentric arc R 4. Coefficients of higher-order curves a 0、 a 1. a 2. a Three independent geometric parameters allow for precise control of the clearance volume. Compared to the claw vacuum pump disclosed in Chinese Patent CN108757464B, the clearance volume of this invention is reduced by 14% to 20% when applied to a claw vacuum pump, and the relative clearance volume is reduced by 12% to 19%, resulting in less residual compressed gas and thus reduced power consumption.

[0166] In the preceding text, according to Figures 8 to 33 The paper details the working process of one of the two working chambers separated by the first claw rotor 2 and the second claw rotor 3, which sequentially serves as the intake chamber 401, the first mixing chamber 402, the compression chamber 403, the exhaust chamber 404, and the second mixing chamber 405. The other working chamber also undergoes the intake, first mixing, compression, exhaust, and second mixing processes. The working processes of the two working chambers are cyclical, and different working processes may be occurring at the same time. For example, when one working chamber is undergoing the intake process, the other working chamber may be undergoing the compression or exhaust process, and vice versa; when one working chamber is undergoing the first mixing process, the other working chamber is undergoing the second mixing process, and vice versa.

[0167] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0168] The above preferred embodiments should not be considered as limitations on the present invention, and the scope of protection of the present invention should be determined by the scope defined in the claims. For those skilled in the art, various improvements and modifications can be made without departing from the spirit and scope of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A symmetrical single-claw rotor, characterized in that: Including two claw rotors with the same cross-sectional profile that can perform synchronous and opposite-direction double-rotation motion around their respective rotation centers; The cross-sectional profile of the claw rotor includes a cycloid, a point, a claw top arc, an eccentric arc, a higher-order curve, a pitch circle arc, a conjugate curve of the higher-order curve, a conjugate curve of the eccentric arc, and a claw bottom arc connected in sequence.

2. A symmetrical single-claw rotor as described in claim 1, characterized in that: Establish a rectangular coordinate system with the rotation center of the claw rotor as the origin, and plot the coordinate system with radius as... R The claw tip circle of 1 has a radius of 1. R The pitch circle and radius of 2 are R The base circle of the 3rd claw has a radius of 3. R 4. Use the eccentric circle as a reference; The shape of the cycloid is determined by the following equation: in, x AB ( t ), y AB ( t ) for cycloid x , y The corresponding coordinates on the axis; t For angle parameters; The shape of the claw tip arc is determined by the following equation: in, x BC ( t ), y BC ( t ( ) is the claw tip arc in x , y The corresponding coordinates on the axis; The shape of the eccentric circular arc is determined by the following equation: in, x CD ( t ), y CD ( t ) is an eccentric circular arc in x , y The corresponding coordinates on the axis; α The central angle of the claw tip arc; The shape of the higher-order curve is determined by the following equation: in, x DE ( t ), y DE ( t ) is a higher-order curve in x , y The corresponding coordinates on the axis; a 0、 a 1. a 2. a 3 represents the coefficients of higher-order curves, determined by the following system of equations: in, β The central angle of the eccentric arc. θ The central angle of a higher-order curve; The shape of the pitch circle arc is determined by the following equation: in, x EF ( t ), y EF ( t ) is the arc of the pitch circle in x , y The corresponding coordinates on the axis; The shape of the conjugate curve of the higher-order curve is determined by the following equation: in, x FG ( t ), y FG ( t () is the conjugate curve of a higher-order curve. x , y The corresponding coordinates on the axis; φ 1 represents the positional parameter of the conjugate curve of the higher-order curve, determined by the following equation: in, f ( t, φ 1) The equation of the envelope of a higher-order curve obtained by the envelope method; The shape of the conjugate curve of the eccentric circular arc is determined by the following equation: in, x GH ( t ), y GH ( t () is the conjugate curve of an eccentric circular arc in x , y The corresponding coordinates on the axis; φ 2 represents the positional parameter of the conjugate curve of the eccentric circular arc, determined by the following equation: in, f ( t, φ 2) The equation of the envelope of the eccentric circular arc is obtained by using the envelope method; The shape of the arc at the bottom of the claw is determined by the following equation: in, x HA ( t ), y HA ( t (The claw bottom arc is in) x , y The corresponding coordinates on the axis.

3. A claw-type fluid machinery, characterized in that: Includes two claw rotors as described in claim 2, the two claw rotors perform synchronous and opposite double rotational motions around their respective rotation centers, and the distance between the rotation centers of the two claw rotors is the diameter of the pitch circle; During the synchronous and opposite double-rotation motion of the two claw rotors, the cycloid, point, claw top arc, eccentric arc, higher-order curve, pitch circle arc, conjugate curve of higher-order curve, conjugate curve of eccentric arc, and claw bottom arc of one claw rotor respectively mesh with the point, cycloid, claw bottom arc, conjugate curve of eccentric arc, conjugate curve of higher-order curve, pitch circle arc, higher-order curve, eccentric arc, and claw top arc of the other claw rotor.

4. A claw-type fluid machine as described in claim 3, characterized in that: It also includes a cylinder (4), a front cover (1), a rear cover (5), an intake port (501), and an exhaust port (502); The cylinder (4) has a pump chamber that accommodates two claw rotors; The front cover (1) and the rear cover (5) are respectively encapsulated at both ends of the cylinder (4); When the two claw rotors perform synchronous and opposite double-rotation motion, they divide the pump chamber into two working chambers; the two working chambers are used for intake, mixing, compression and exhaust respectively. The air intake (501) is provided on at least one of the front end cover (1) and the rear end cover (5); The exhaust port (502) is provided on at least one of the front end cover (1) and the rear end cover (5); The air intake (501) and the exhaust (502) are respectively provided for two claw rotors.

5. A claw-type fluid machine as described in claim 4, characterized in that: The cross-sectional profile of the pump chamber includes two connected circular arcs; the radii of the two circular arcs are the same and slightly larger than the radius of the claw top circle, and the center distance between the two circular arcs is the diameter of the pitch circle.

6. A claw-type fluid machine as described in claim 5, characterized in that: A rectangular coordinate system is established with the rotation center of one of the claw rotors as the origin. The shapes of the two circular arcs of the pump cavity are determined by the following equations: in, x MNO ( t ), y MNO ( t ) is one segment of an arc in x , y The corresponding coordinates on the axis x OPM ( t ), y OPM ( t ( ) is another arc in x , y The corresponding coordinates on the axis; R 9 represents the radius corresponding to the arc of the pump cavity.

7. A claw-type fluid machine as described in claim 4, characterized in that: The air intake (501) is arc-shaped; The starting position of the intake port (501) is determined by the cycloid of the claw rotor at the end of the mixing process; The end position of the intake port (501) is determined by the conjugate curve of the higher-order curve of the claw rotor corresponding to the start time of the mixing process.

8. A claw-type fluid machine as described in claim 7, characterized in that: The cross-sectional profile of the air intake (501) includes a second inner arc, a second end arc one, a second outer arc, and a second end arc two connected in sequence. Establish a rectangular coordinate system with the rotation center of one of the claw rotors as the origin, and plot the coordinates with radii of... R The pitch circle and radius of 2 are R Use the claw bottom circle of number 3 as a reference; The shape of the second inner arc is determined by the following equation: in, x kl ( t ), y kl ( t () is the second inner arc in x , y The corresponding coordinates on the axis; R 5 is the radius corresponding to the second inner arc, and R 5 ＞R 3; The shape of the second outer arc is determined by the following equation: in, x ij ( t ), y ij ( t () is the second outer arc in x , y The corresponding coordinates on the axis; R 6 is the radius corresponding to the second outer arc. R 6= R 5+ l 1, l 1 represents the radial distance between the second inner arc and the second outer arc, and R 5< R 6< R 2.

9. A claw-type fluid machine as described in claim 4, characterized in that: The exhaust port (502) is arc-shaped; The starting position of the exhaust port (502) is determined by the pressure ratio, internal ratio and intake volume of the claw fluid machinery, and is constrained by the conjugate curve of the corresponding claw rotor's higher-order curve. The end position of the exhaust port (502) is determined by the cycloid of the claw rotor at the start of the mixing process.

10. A claw-type fluid machine as described in claim 9, characterized in that: The cross-sectional profile of the exhaust port (502) includes a first inner arc, a first end arc one, a first outer arc, and a first end arc two connected in sequence. Establish a rectangular coordinate system with the rotation center of one of the claw rotors as the origin, and plot the coordinates with radii of... R The pitch circle and radius of 2 are R Use the claw bottom circle of number 3 as a reference; The shape of the first inner arc is determined by the following equation: in, x IJ ( t ), y IJ ( t () is the first inner arc in x , y The corresponding coordinates on the axis; R 7 is the radius corresponding to the first inner arc, and R 7 ＞R 3; The shape of the first outer arc is determined by the following equation: in, x KL ( t ), y KL ( t ) is the first outer arc in x , y The corresponding coordinates on the axis; R 8 represents the radius corresponding to the first outer arc. R 8= R 7+ l 2, l 2 is the radial distance between the first inner arc and the first outer arc, and R 7< R 8< R 2.

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