CN112727755A - High-strength vortex tooth and high-strength vortex disc structure - Google Patents
High-strength vortex tooth and high-strength vortex disc structure Download PDFInfo
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- CN112727755A CN112727755A CN202110055340.4A CN202110055340A CN112727755A CN 112727755 A CN112727755 A CN 112727755A CN 202110055340 A CN202110055340 A CN 202110055340A CN 112727755 A CN112727755 A CN 112727755A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
- F04C18/0284—Details of the wrap tips
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
The invention provides a high-strength vortex tooth, which is characterized in that a vortex tooth wall is formed by a vortex tooth profile line structure, and particularly, the vortex tooth wall is sequentially provided with a main section, a transition section and an avoiding section from the center to the tail end; the delta T is the thickness variation of the vortex tooth wall relative to the main section, the thickness of the main section is unchanged, and the delta T is 0; the thickness of the transition section is gradually reduced, and the Delta T is gradually increased to meet the condition that 0 is less than the Delta T and less than 2T; the thickness of the avoidance section is unchanged, the Delta T is stable all the time, and the requirement that the Delta T is 2T is met. And the high-strength vortex plate structure comprises a fixed vortex plate and a movable vortex plate, wherein the phase angle of vortex teeth of the fixed vortex plate and the movable vortex plate is 180 degrees different, and the vortex teeth on the fixed vortex plate and the vortex teeth on the movable vortex plate are both high-strength vortex teeth. The high-strength vortex plate structure and the high-strength vortex teeth can effectively solve the problems of high temperature at the center of the vortex teeth and deformation and collision in the running process of the vortex teeth, and greatly improve the reliability and the manufacturing process stability of a vortex compressor.
Description
Technical Field
The invention relates to the technical field of air conditioning equipment, in particular to a high-strength scroll wrap and a high-strength scroll plate structure using the same in a scroll compressor.
Background
Scroll compressors are widely used in air conditioning equipment because of their small size, high efficiency, and smooth operation. The most commonly used scroll compressor theory of operation at present is through the mutual cooperation of static vortex dish and moving vortex dish, moves the vortex dish and installs on the eccentric portion of bent axle, and under the drive of motor drive bent axle, the eccentric volume of bent axle makes the continuous crescent moon chamber that moves the vortex dish and can stabilize and breathe in, compress and carminative with static vortex dish. The temperature of the vortex line is gradually increased from the outer side to the center in the operation process of the compressor, and the acting force applied to the vortex tooth is gradually increased from the outer side to the center along with the progress of a refrigerant of the compressor, so that the deformation amount of the vortex tooth at the center of the vortex plate is the largest in the operation state of high temperature and large acting force.
At present, with the rapid development of variable frequency control modules, material technologies and processing technologies, the market has higher and higher requirements on the compressor, and the compressor is required to have higher rotating speed and larger capacity. Because of the increased demand, it is important to design and increase the strength of the key component part of the scroll wraps of the scroll compressor. To meet the market demand, the industry commonly makes: the first is that the physical displacement of the scroll plate is improved by improving the height of the scroll wrap on the premise of the same compressor cylinder diameter; the second is by increasing the rotational speed of the compressor. In either variation, the challenge presented to the scroll wrap is very severe. Except that the problems of high temperature and large acting force at the center of the scroll wrap need to be solved, because of the increase of the wrap height and the increase of the rotating speed, the outer part of the scroll wrap is under the action of larger centrifugal force, so that the deformation is large, the movable scroll plate collides with the scroll wrap of the fixed scroll plate, and the reliability of the scroll compressor is seriously influenced. There is therefore a need for improvement.
Disclosure of Invention
The invention aims to solve the technical problem of large deformation of the scroll wrap, and provides a high-strength scroll wrap and a high-strength scroll structure.
The purpose of the invention can be realized by the following technical scheme:
the utility model provides a high strength scroll wrap, it is formed by the scroll profile line structure, the scroll profile line structure is gradually involute, the central portion that connects gradually and is crossed the crossover line and interior line is involute, and the outer line is involute and interior line involute cooperation sets up and forms the scroll tooth wall, and the central portion crosses the center that the crossover line is located the scroll tooth wall, its characterized in that: the vortex tooth wall sequentially comprises a main section, a transition section and an avoiding section from the center to the tail end; defining delta T as the thickness variation of the vortex tooth wall relative to the main section, wherein the thickness of the main section is unchanged, and the thickness variation delta T is 0; the thickness of the transition section is gradually thinned from the front end to the tail end, and the thickness variation quantity delta T is gradually increased from the front end to the tail end, so that the transition section with the thickness variation quantity delta T satisfying 0 & ltdelta T & lt 2T is formed; the thickness of the avoidance section is unchanged, and the thickness variation quantity delta T is stable from the front end to the tail end all the time, so that the avoidance section with the thickness variation quantity delta T being 2T is formed.
Preferably, the present invention sets the parameters of the scroll tooth profile as follows:
lambda 0 is the expansion angle of the external line involute at the starting point a of the main section;
λ 5 is the expansion angle of the inner line involute at the main section terminal point f;
lambda 7 is an expansion angle of the inner line involute at the avoiding section terminal point h;
theta is a parameter of the spread angle of any point on the vortex tooth profile structure;
the thickness variation of the inner side wall of the vortex tooth wall relative to the inner side wall of the main section is equal to the thickness variation of the outer side wall of the vortex tooth wall relative to the outer side wall of the main section, and the thickness variation is delta and meets the requirement that delta is delta T/2;
the thickness change value of the inner side wall of the avoidance section relative to the inner side wall of the main section is equal to the thickness change value of the outer side wall of the avoidance section relative to the outer side wall of the main section and is t;
when the outer line involute is in the main section, the requirements are as follows: λ 0 is not less than θ is not less than λ 1, and Δ is 0;
when the outer line involute is in the transition section, the requirements are as follows: λ 1 < θ ≦ λ 2, Δ ═ t (θ - λ 1)/(λ 2- λ 1);
the outer line involute meets the following requirements when avoiding the section: theta is more than lambda 2 and less than or equal to lambda 3, and delta is t;
the interior line is gradually burst into the seams when the main section, satisfies: λ 4 is not less than θ is not more than λ 5, and Δ is 0;
the interior line is gradually burst into the seams when the changeover portion, satisfies: λ 5 < θ ≦ λ 6, Δ ═ t (θ - λ 5)/(λ 6- λ 5);
interior line gradually bursts at seams when dodging the section, satisfies: λ 6 < θ ≦ λ 7, and Δ ═ t.
Preferably, the present invention further sets the parameters of the scroll tooth profile as follows:
a is the base circle radius of the vortex tooth-shaped line structure;
alpha is the molded line included angle of the outer line involute and the inner line involute;
the outer line involute satisfies in an X-Y coordinate system:
X1(θ)＝A[cos(θ)+(θ-△/A)sin(θ)]
Y1(θ)＝A[sin(θ)-(θ-△/A)cos(θ)]
λ0≤θ≤λ1，△＝0；
λ1＜θ≤λ2，△＝t(θ-λ1)/(λ2-λ1)；
λ2＜θ≤λ3，△＝t；
the inner line involute satisfies in an X-Y coordinate system:
X2(θ)＝A[cos(θ)+(θ-α+△/A)sin(θ)]
Y2(θ)＝A[sin(θ)-(θ-α+△/A)cos(θ)]
λ4≤θ≤λ5，△＝0；
λ5＜θ≤λ6，△＝t(θ-λ5)/(λ6-λ5)；
λ6＜θ≤λ7，△＝t。
preferably, the trailing end of the wrap wall of the present invention has at least 1 trailing end step of reduced height. Furthermore, the tail end step part of the vortex tooth wall comprises a first step part and a second step part, the heights of the first step part and the second step part are sequentially reduced.
Preferably, the transition line of the central part of the vortex tooth profile line structure comprises a first central part transition circle and a second central part transition circle which are connected through ends, the other end of the first central part transition circle is connected with an outer line involute, the other end of the second central part transition circle is connected with an inner line involute, and the inner wall of the central part of the vortex tooth wall is provided with a central part cutting groove which is formed by cutting the part from the top of the vortex tooth wall to the part near the middle part.
Preferably, the present invention further sets the parameters of the scroll tooth profile as follows:
r is the radius of a first central transition circle in the central transition line;
r is the radius of the second central transition circle in the central transition line;
(x0，y0) Is the center coordinate of the first heart transition circle, then (-x)0’，-y0') is the center coordinates of the second center transition circle;
λ 8 is the expansion angle of the first center transition circle and the second center transition circle connecting point B on the first center transition circle;
λ 0' is the expansion angle of the connection point a of the first core transition circle and the outer line involute, and λ 0 ═ λ 0;
λ 8 'is the expansion angle of the second center transition circle and the first center transition circle connecting point B' on the second center transition circle, and λ 8 ═ λ 8+ pi;
λ 4' is the expansion angle of the connection point C of the second center transition circle and the inner line involute, and λ 4 ═ λ 4;
theta is a parameter of the spread angle of any point on the vortex tooth profile structure;
the first heart transition circle satisfies in the X-Y coordinate system:
X3(θ)＝Rsin(θ)-x0
Y3(θ)＝-[Rcos(θ)-y0]
λ8≤θ≤λ0；
the second center transition circle satisfies in the X-Y coordinate system:
X4(θ)＝rsin(θ)+x0’
Y4(θ)＝-[rcos(θ)+y0’]
(λ8+π)≤θ≤λ4。
a high-strength vortex plate structure comprises a static vortex plate and a movable vortex plate, wherein the phase angle of vortex teeth of the static vortex plate and the movable vortex plate is 180 degrees, and the vortex teeth are buckled up and down, and the vortex teeth on the static vortex plate and the vortex teeth on the movable vortex plate are high-strength vortex teeth, wherein the vortex teeth walls sequentially comprise a main section, a transition section and an avoiding section from the center to the tail end.
Preferably, in the high-strength scroll structure of the present invention, the trailing end of the wrap wall of the wrap on the orbiting scroll has at least 1 trailing end step portion with a reduced height.
Preferably, in the high-strength scroll structure according to the present invention, each of the inner wall of the core of the wrap on the fixed scroll and the inner wall of the core of the wrap on the movable scroll has a core-cut groove which is cut from a top portion to a portion near the middle portion of the wrap wall.
The invention has the following prominent substantive features and remarkable progress:
1. in the high-strength vortex tooth, the problems of large acting force and deformation and collision of the outer part of the vortex tooth caused by centrifugal force are effectively solved through the avoidance section with the stably changed thickness, and the main section of the vortex tooth wall is smoothly and slowly transited to the avoidance section through the transition section with the gradually increased thickness change, so that the smoothness of the surfaces of the inner side wall and the outer side wall of the vortex tooth wall is effectively ensured.
2. In the high-strength scroll wrap, the thickness change value t of the avoiding section of the scroll wrap wall and the arc length of the avoiding section (namely the positions of the starting point and the end point of the avoiding section) can be artificially and approximately given as t between 0.02 and 0.1mm, and the arc length is 0.03 to 0.06 times of the total arc length of the scroll wrap wall, and the CAE simulation analysis result of a scroll compressor under the conditions of maximum load and maximum rotating speed can also be adopted for optimization.
3. According to the invention, by setting delta to be delta T/2', the thickness variation of the inner side wall of the vortex tooth wall is 0.5 times of delta T, and the thickness variation of the outer side wall of the vortex tooth wall is 0.5 times of delta T, so that the thickness of the vortex tooth wall is uniformly optimized by the inner side wall and the outer side wall of the vortex tooth wall, and the smoothness of the surfaces of the inner side wall and the outer side wall of the vortex tooth wall is further effectively ensured. Of course, "the thickness variation Δ of the inner side wall of the scroll tooth wall is equal to k Δ T, the thickness variation Δ of the outer side wall of the scroll tooth wall is equal to (1-k) Δ T, where k is not less than 0 and not more than 1", may be set, and the thickness of the scroll tooth wall may be optimized by the inner and outer side walls of the scroll tooth wall, respectively, so as to realize the optimization improvement of the transition section and the avoidance section of the scroll tooth wall in response to deformation and collision.
4. In the high-strength vortex tooth, the tail end step part plays a role in increasing the strength of the tail end of the vortex tooth wall; and further, on the premise of ensuring the strength of the central part of the vortex tooth wall through the central part cutting groove, the exhaust resistance is effectively reduced, the exhaust efficiency is improved, and the temperature of the vortex central part is further effectively reduced.
5. According to the high-strength scroll plate structure, the deformation of the scroll teeth of the movable scroll plate and the fixed scroll plate is reduced by adopting the high-strength scroll teeth, the failure of the scroll teeth of the scroll compressor in the high-speed operation process is effectively solved, and the overall reliability of the scroll compressor is improved.
Drawings
Fig. 1 and 2 are schematic structural views of a high strength scroll wrap according to embodiment 1.
FIG. 3 is a partial schematic view of the high strength wrap of example 1.
FIG. 4 is a schematic view of the scroll wall core of the high strength scroll of example 1.
Fig. 5 and 6 are schematic views of the structure of the high strength wrap of embodiment 2.
FIG. 7 is a schematic view of the trailing end of the wrap wall of the high strength wrap of embodiment 2.
Fig. 8 is a schematic view of the structure of a high-strength scroll according to example 3.
Detailed Description
The invention will be further explained with reference to the drawings.
Example 1
Referring to fig. 1 to 4, a high strength scroll wrap is formed of a scroll tooth profile structure including an outer involute 1, a central transition line and an inner involute 2 which are sequentially connected, the outer involute 1 and the inner involute 2 being cooperatively arranged to form a scroll wall 10.
The central transition line is positioned at the central part of the vortex tooth wall 10 and comprises a first central part transition circle 3 and a second central part transition circle 4 which are connected through ends, the other end of the first central part transition circle 3 is connected with an outer line involute 1, and the other end of the second central part transition circle 4 is connected with an inner line involute 2. Referring specifically to fig. 4, the inner wall of the core of the wrap wall 10 has a core slot 16, the core slot 16 being cut from the apex to near the middle of the wrap wall 10.
The volute teeth wall 10 comprises a main section 11, a transition section 12 and an avoidance section 13 from the center to the tail end in sequence.
Referring specifically to fig. 2 and 3, the parameters of the scroll tooth profile are set for the outer involute 1 and the inner involute 2, and an involute curve model is established as follows:
a is the base circle radius of the vortex tooth-shaped line structure;
alpha is the molded line included angle of the outer line involute 1 and the inner line involute 2;
λ 0 is the expansion angle of the external involute 1 at the starting point a of the main section 11;
λ 5 is the expansion angle of the inner line involute 2 at the end point f of the main section 11;
λ 7 is an expansion angle of the inner line involute 2 at the terminal point h of the avoidance section 13;
theta is a parameter of the spread angle of any point on the vortex tooth profile structure;
Δ T is the thickness variation of the scroll tooth wall 10 with respect to the main section 11;
the thickness variation of the inner side wall of the vortex tooth wall 10 relative to the inner side wall of the main section 11 is equal to the thickness variation of the outer side wall of the vortex tooth wall 10 relative to the outer side wall of the main section 11, and the requirement that the thickness variation is equal to delta T/2 is met;
the thickness change value of the inner side wall of the avoidance section 13 relative to the inner side wall of the main section 11 is equal to the thickness change value of the outer side wall of the avoidance section 13 relative to the outer side wall of the main section 11 and is t;
the outer line involute 1 satisfies the following conditions in an X-Y coordinate system:
X1(θ)＝A[cos(θ)+(θ-△/A)sin(θ)]
Y1(θ)＝A[sin(θ)-(θ-△/A)cos(θ)]
λ0≤θ≤λ1，△＝0；
λ1＜θ≤λ2，△＝t(θ-λ1)/(λ2-λ1)；
λ2＜θ≤λ3，△＝t；
the inner line involute 2 satisfies in the X-Y coordinate system:
X2(θ)＝A[cos(θ)+(θ-α+△/A)sin(θ)]
Y2(θ)＝A[sin(θ)-(θ-α+△/A)cos(θ)]
λ4≤θ≤λ5，△＝0；
λ5＜θ≤λ6，△＝t(θ-λ5)/(λ6-λ5)；
λ6＜θ≤λ7，△＝t。
when the outer line involute 1 is in the main section 11, the requirements are as follows: λ 0 is not less than θ is not less than λ 1, and Δ is 0;
when the outer line involute 1 is positioned at the transition section 12,
satisfies the following conditions: λ 1 < θ ≦ λ 2, Δ ═ t (θ - λ 1)/(λ 2- λ 1);
the outer line involute 1 meets the following requirements when avoiding the section 13: theta is more than lambda 2 and less than or equal to lambda 3, and delta is t;
when the inner line involute 2 is arranged at the transition section 12,
satisfies the following conditions: λ 5 < θ ≦ λ 6, Δ ═ t (θ - λ 5)/(λ 6- λ 5);
Through the cooperation of the outer line involute 1 and the inner line involute 2 respectively at the main section 11, the transition section 12 and the avoiding section 13, the following characteristics are formed:
the thickness of the main section 11 is constant, and the thickness variation quantity Delta T is 0;
the thickness of the transition section 12 is gradually reduced from the front end to the tail end, and the thickness variation Delta T is gradually increased from the front end to the tail end to form the transition section 12 with the thickness variation Delta T satisfying 0 & lt Delta T & lt 2T;
the thickness of the avoidance section 13 becomes thinner gradually from the front end to the tail end, and the thickness variation quantity delta T is stable all the time from the front end to the tail end, so that the avoidance section 13 with the thickness variation quantity delta T being 2T is formed.
Referring specifically to fig. 2, the parameters of the scroll tooth profile are set for the first and second center transition circles 3 and 4 and the transition circle model is established as follows:
r is the radius of the first center transition circle 3 in the center transition line;
r is the radius of the second center transition circle 4 in the center transition line;
(x0，y0) Is the center coordinate of the first heart transition circle 3, then (-x)0’，-y0') is a second heart transitionThe center coordinates of circle 4;
λ 8 is the flare angle of the connection point B of the first central transition circle 3 and the second central transition circle 4 on the first central transition circle 3;
λ 0' is the expansion angle of the connection point a of the first core transition circle 3 and the outer involute 1, and λ 0 ═ λ 0;
λ 8 'is the expansion angle of the connection point B' of the second core transition circle 4 and the first core transition circle 3 on the second core transition circle 4, and λ 8 ═ λ 8+ pi;
λ 4' is the flare angle of the connection point C of the second core transition circle 4 and the inner line involute 2, and λ 4 ═ λ 4;
theta is a parameter of the spread angle of any point on the vortex tooth profile structure;
the first heart transition circle 3 then satisfies in the X-Y coordinate system:
X3(θ)＝Rsin(θ)-x0
Y3(θ)＝-[Rcos(θ)-y0]
λ8≤θ≤λ0；
the second heart transition circle 4 then satisfies in the X-Y coordinate system:
X4(θ)＝rsin(θ)+x0’
Y4(θ)＝-[rcos(θ)+y0’]
(λ8+π)≤θ≤λ4。
in addition, in this embodiment, the form of the transition line MN of the tail end of the scroll tooth wall 10 is not limited, and may be an arc, a straight line with a rounded corner, or the like, which mainly plays a role in transition connecting the inner line involute and the outer line involute.
Example 2
Referring to fig. 5 to 7, the high strength wrap of the present embodiment is different from embodiment 1 in that: the trailing end of the wrap wall 10 in this embodiment has a first step 14 and a second step 15 of successively decreasing height. The first step portion 14 and the second step portion 15 do not participate in the meshing compression, and they function to increase the strength of the scroll wrap wall 10.
In addition, in this embodiment, the forms of the tail end transition line DE, the tail end transition line FG, and the tail end transition line MN of the tail end of the scroll tooth wall 10 are not limited, and may be arcs, straight lines with rounded corners, or the like, which mainly play a role in connecting the inner line involute and the outer line involute.
Example 3
Referring to fig. 8, a high-strength scroll structure includes a fixed scroll 5 and a movable scroll 6, where the phase angles of the wraps of the fixed scroll 5 and the movable scroll 6 are different by 180 degrees and are buckled up and down, the wrap on the fixed scroll 5 adopts the high-strength wrap of embodiment 1, and the wrap on the movable scroll 6 adopts the high-strength wrap of embodiment 2.
The high-strength scroll structure of the embodiment can increase the strength of the scroll center and reduce the exhaust resistance through the first center transition circle 3, the second center transition circle 4 and the matching center cutting groove 16 on the premise that the compression internal volume ratio of the scroll and the suction volume and the height of the scroll wrap are not changed; meanwhile, collision of the tail end of the scroll wrap when the scroll wrap operates at a high speed is reduced through the avoidance section 13, effective avoidance of the movable scroll wrap and the static scroll wrap is achieved through stable thickness variation of the scroll wrap wall, stress is reduced, deformation of the movable scroll wrap and the static scroll wrap is reduced, the problem that the scroll wrap of the scroll compressor fails in the high-speed operation process is effectively solved, and the overall reliability of the scroll compressor is improved.
Claims (10)
1. The utility model provides a high strength vortex tooth, it is formed by vortex tooth profile line structure, vortex tooth profile line structure is gradually involute (1) including the outer line that connects gradually, the central portion crosses the crossover line and interior line (2) that gradually involute, and the outer line is involute (1) and interior line (2) cooperation sets up and forms vortex tooth wall (10), and the central portion crosses the crossover line and is located the central portion of vortex tooth wall (10), its characterized in that: the vortex tooth wall (10) sequentially comprises a main section (11), a transition section (12) and an avoidance section (13) from the center to the tail end;
defining delta T as the thickness variation of the vortex tooth wall (10) relative to the main section (11), wherein the thickness of the main section (11) is constant, and the thickness variation delta T is 0;
the thickness of the transition section (12) is gradually reduced from the front end to the tail end, and the thickness variation Delta T is gradually increased from the front end to the tail end to form the transition section (12) with the thickness variation Delta T satisfying 0 & ltDelta T & lt 2T;
the thickness of the avoidance section (13) is constant, and the thickness variation quantity delta T is stable from the front end to the tail end, so that the avoidance section (13) with the thickness variation quantity delta T being 2T is formed.
2. The high strength scroll wrap of claim 1 wherein the scroll tooth pattern is characterized by the following parameters:
lambda 0 is the expansion angle of the outer line involute (1) at the starting point a of the main section (11);
lambda 1 is the expansion angle of the outer line involute (1) at the end point b of the main section (11);
lambda 2 is the expansion angle of the outer line involute (1) at the end point c of the transition section (12);
lambda 3 is an expansion angle of the outer line involute (1) at the end point d of the avoidance section (13);
lambda 4 is the expansion angle of the inner line involute (2) at the starting point e of the main section (11);
lambda 5 is an expansion angle of the inner line involute (2) at the terminal point f of the main section (11);
lambda 6 is the expansion angle of the inner line involute (2) at the end point g of the transition section (12);
lambda 7 is an expansion angle of the inner line involute (2) at the terminal h of the avoidance section (13);
theta is a parameter of the spread angle of any point on the vortex tooth profile structure;
the thickness variation of the inner side wall of the vortex tooth wall (10) relative to the inner side wall of the main section (11) and the thickness variation of the outer side wall of the vortex tooth wall (10) relative to the outer side wall of the main section (11) are equal to delta, and delta is equal to delta T/2;
the thickness change value of the inner side wall of the avoidance section (13) relative to the inner side wall of the main section (11) is equal to the thickness change value of the outer side wall of the avoidance section (13) relative to the outer side wall of the main section (11) and is t;
the outer line involute (1) meets the following requirements in the main section (11): λ 0 is not less than θ is not less than λ 1, and Δ is 0;
when the outer line involute (1) is arranged at the transition section (12),
satisfies the following conditions: λ 1 < θ ≦ λ 2, Δ ═ t (θ - λ 1)/(λ 2- λ 1);
the outer line involute (1) meets the following requirements when avoiding the section (13): theta is more than lambda 2 and less than or equal to lambda 3, and delta is t;
interior line involute (2) when main section (11), satisfy: λ 4 is not less than θ is not more than λ 5, and Δ is 0;
when the inner line involute (2) is arranged on the transition section (12),
satisfies the following conditions: λ 5 < θ ≦ λ 6, Δ ═ t (θ - λ 5)/(λ 6- λ 5);
interior line involute (2) satisfies when dodging section (13): λ 6 < θ ≦ λ 7, and Δ ═ t.
3. The high strength scroll wrap of claim 2 wherein the scroll tooth pattern is characterized by the following parameters:
a is the base circle radius of the vortex tooth-shaped line structure;
alpha is the molded line included angle of the outer line involute (1) and the inner line involute (2);
the outer line involute (1) satisfies the following conditions in an X-Y coordinate system:
X1(θ)＝A[cos(θ)+(θ-△/A)sin(θ)]
Y1(θ)＝A[sin(θ)-(θ-△/A)cos(θ)]
λ0≤θ≤λ1，△＝0；
λ1＜θ≤λ2，△＝t(θ-λ1)/(λ2-λ1)；
λ2＜θ≤λ3，△＝t；
the inner line involute (2) satisfies in an X-Y coordinate system:
X2(θ)＝A[cos(θ)+(θ-α+△/A)sin(θ)]
Y2(θ)＝A[sin(θ)-(θ-α+△/A)cos(θ)]
λ4≤θ≤λ5，△＝0；
λ5＜θ≤λ6，△＝t(θ-λ5)/(λ6-λ5)；
λ6＜θ≤λ7，△＝t。
4. the high strength scroll wrap of claim 1, wherein: the trailing end of the wrap wall (10) has at least 1 trailing end step of reduced height.
5. The high strength scroll wrap of claim 4, wherein: the tail end step part of the vortex tooth wall (10) comprises a first step part (14) and a second step part (15) with the heights being sequentially reduced.
6. The high strength scroll wrap of claim 1 or 2 or 3 or 4 or 5 wherein: vortex tooth profile line structure central part transition line is including first heart transition circle (3) and second heart transition circle (4) that the end is connected, and the outer line involute (1) is connected to the other end of first heart transition circle (3), and the inner line involute (2) is connected to the other end of second heart transition circle (4), and the heart inner wall of vortex tooth wall (10) has heart grooving (16), heart grooving (16) are cut by the top of vortex tooth wall (10) to near part in middle part and are formed.
7. The high strength scroll wrap of claim 6 wherein the scroll tooth pattern is characterized by the following parameters:
r is the radius of the first central transition circle (3) in the central transition line;
r is the radius of the second central transition circle (4) in the central transition line;
(x0，y0) Is the center coordinate of the first heart transition circle (3), then (-x)0’，-y0') is the center coordinates of the second central transition circle (4);
lambda 8 is the expansion angle of the connection point B of the first central transition circle (3) and the second central transition circle (4) on the first central transition circle (3);
lambda 0' is the expansion angle of the connection point A of the first heart transition circle (3) and the outer line involute (1),
and λ 0' ═ λ 0;
λ 8 'is the expansion angle of the second core transition circle (4) on the second core transition circle (4) and the connection point B' of the first core transition circle (3), and λ 8 ═ λ 8+ pi;
lambda 4' is the expansion angle of the connecting point C of the second central transition circle (4) and the inner line involute (2),
and λ 4' ═ λ 4;
theta is a parameter of the spread angle of any point on the vortex tooth profile structure;
the first heart transition circle (3) then fulfils in an X-Y coordinate system:
X3(θ)＝Rsin(θ)-x0
Y3(θ)＝-[Rcos(θ)-y0]
λ8≤θ≤λ0；
the second central transition circle (4) then fulfils in an X-Y coordinate system:
X4(θ)＝rsin(θ)+x0’
Y4(θ)＝-[rcos(θ)+y0’]
(λ8+π)≤θ≤λ4。
8. the utility model provides a high strength vortex dish structure, its includes quiet vortex dish (5) and moves vortex dish (6), and the vortex tooth phase angle phase difference 180 degrees, the upper and lower looks of quiet vortex dish (5) and moving vortex dish (6) are detained, its characterized in that: the high-strength vortex teeth of the claim 1, the claim 2 or the claim 3 are adopted in the vortex teeth on the static vortex plate (5) and the vortex teeth on the movable vortex plate (6).
9. The high strength scroll structure according to claim 8, wherein: the tail end of the upper scroll wrap of the movable scroll (6) is provided with at least 1 tail end step part with reduced height.
10. The high strength scroll structure according to claim 8 or 9, wherein: the inner wall of the center of the upper scroll wrap of the fixed scroll (5) and the inner wall of the center of the upper scroll wrap of the movable scroll (6) are both provided with a center cutting groove (16), and the center cutting groove (16) is formed by cutting the part from the top to the vicinity of the middle part of the scroll wrap wall (10).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110055340.4A CN112727755A (en) | 2021-01-15 | 2021-01-15 | High-strength vortex tooth and high-strength vortex disc structure |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7191246B2 (en) | 2019-11-07 | 2022-12-16 | 三菱電機株式会社 | Scroll compressor and refrigeration cycle equipment |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7191246B2 (en) | 2019-11-07 | 2022-12-16 | 三菱電機株式会社 | Scroll compressor and refrigeration cycle equipment |
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