CN113738643A

CN113738643A - Semi-arc air conditioner compressor and air conditioner thereof

Info

Publication number: CN113738643A
Application number: CN202111095721.1A
Authority: CN
Inventors: 孔祥真
Original assignee: Individual
Current assignee: Sanhe Tongfei Refrigeration Co ltd
Priority date: 2021-04-06
Filing date: 2021-09-17
Publication date: 2021-12-03
Anticipated expiration: 2041-09-17
Also published as: CN113738643B; CN113653644A; CN113738648A; CN113738648B; CN113775522A; CN113653644B

Abstract

The semi-arc air-conditioning compressor comprises a compressor main body and a motor, wherein a shell is arranged on the peripheries of the compressor main body and the motor, an air inlet connecting pipe and an air outlet connecting pipe are arranged on the shell, the compressor main body consists of an air cylinder and an air cylinder chamber, and the air cylinder is arranged in the air cylinder chamber; an eccentric driving mechanism is arranged on an output shaft of the motor, a chassis is arranged on the cylinder chamber, an air inlet is formed in the cylinder chamber, and the air inlet is communicated with the air inlet connecting pipe; the cylinder is formed by meshing a static disc and a moving disc, and the static disc is fixedly connected with the shell or the cylinder chamber. The revolution matching surface of one cylinder only has two or two pairs of arc-shaped bodies, the axial sections of the matching surfaces of the arc-shaped bodies are both standard semicircles or the combination of the standard semicircles, the back plate and the cover plate can be standard whole circles or parts of the standard whole circles, the manufacturing process is simple, the mechanical processing is very easy, and further compared with a scroll compressor, the compressor disclosed by the invention has the advantages that the manufacturing process is simplified, and the manufacturing cost is greatly reduced.

Description

Semi-arc air conditioner compressor and air conditioner thereof

Technical Field

The invention relates to the technical field of air conditioner compressors, in particular to a semi-arc air conditioner compressor and an air conditioner thereof.

Background

Among various air conditioning compressors, the scroll compressor has been spotlighted with higher efficiency and more compact volume and less vibration. However, the scroll members of the movable scroll and the stationary scroll of the scroll compressor are formed in a scroll shape, and generally have a multi-turn scroll composition, and thus, the manufacturing process is difficult, and the manufacturing cost is high. Therefore, in the case of maintaining many advantages of the scroll compressor, how to provide a more preferable structure, which makes it easier to manufacture, and improves the production efficiency, thereby reducing the manufacturing cost becomes a key point of research by those skilled in the art.

Disclosure of Invention

In order to solve the above problems, an object of the present invention is to provide a semi-arc air conditioner compressor, which has substantially the same efficiency and vibration as a scroll compressor, but has a greatly simplified structure of a moving plate and a stationary plate of an air cylinder, and compression cylinder parts such as the stationary plate and the moving plate are all composed of semi-arc and arc structures, and are easy to process. Similarly, the air conditioner provided with the semi-arc air conditioner compressor has the advantages.

The technical scheme adopted by the invention for solving the technical problems is as follows: the semi-arc air conditioner compressor is a totally-enclosed air conditioner compressor and is mainly used in the field of household appliances such as household air conditioner refrigeration equipment. The semi-arc air conditioner compressor comprises a compressor main body and a motor 9. The motor 9 provides a rotational driving force to the compressor body. The compressor body and the motor 9 are peripherally provided with a shell 2, and the shell 2 is a totally-enclosed shell. The shell 2 can protect the compressor main body and the motor 9, and meanwhile, the whole structure of the compressor is convenient to fix and seal, so that the whole compressor is more compact, and the compressor is convenient to install in an air conditioning system for use. The housing 2 is provided with an intake connection pipe 24 and an exhaust connection pipe 29. The compressor body is composed of a cylinder 1 and a cylinder chamber 4, and the cylinder 1 is mounted in the cylinder chamber 4. An eccentric driving mechanism is arranged on an output shaft of the motor 9. The cylinder chamber 4 has two schemes: one is that the cylinder chamber 4 only has a chassis 43, the chassis 43 can be fixedly connected with the shell 2, and the cover plate 101 of the cylinder 1 is fixedly connected with the shell 2; alternatively, the cylinder chamber 4 is formed by connecting the base plate 43 and the cylindrical cylinder chamber wall 40, and the cover plate 101 of the cylinder 1 is fixedly connected to the upper part of the cylinder chamber wall 40. The cylinder chamber 4 is provided with an air inlet 42, and the air inlet 42 is communicated with the air inlet connecting pipe 24 to form an air inlet passage for supplying air to the cylinder 1. In order to facilitate the heat dissipation of the motor 9, the motor 9 is usually disposed below the cylinder chamber 4, so that the air in the housing forms an up-and-down convection circulation to cool the lower motor and the bearing.

As shown in fig. 20, the cylinder 1 is constituted by engaging a stationary plate 10 and a movable plate 11. The stationary disk 10 can be fixedly connected to the housing 2 or the cylinder chamber 4. The stationary plate 10 is composed of a semicircular arc plate b and a cover plate 101, and the movable plate 11 is composed of a circular plate a and a back plate 111. The static disc 10 and the movable disc 11 are meshed with the reverse cutting circular plate a through a semicircular arc plate b. A circular plate a and a semicircle board b of cutting against cooperate and form a cylinder circular structure. The semicircular arc plate b and the reverse cutting circular plate a can be matched with the cover plate or the back plate together to form a closed air cavity ab. The number of the air cylinders is determined by the number of the air chambers ab, for example, only one set of the circular plate a and the semicircular plate b which are reversely cut in one air cylinder 1 form one air chamber ab is called a single air cylinder, and for example, two sets of the circular plate a and the semicircular plate b which are reversely cut in one air cylinder 1 form two air chambers ab are called double air cylinders. Usually, there are two air chambers ab in one cylinder 1, so, the following three structural forms of the stationary disc are described by taking a double cylinder as an example: full open type quiet dish, semi-open type quiet dish and totally enclosed quiet dish:

as shown in fig. 48, the fully open type stationary disc 10 is composed of a first stationary disc semi-circular arc 102, a second stationary disc semi-circular arc 103 and a cover plate 101 disposed radially thereon, at this time, the cover plate 101 is actually an entity extending radially from the stationary disc

semi-circular arc

102 or 103, and the cover plate 10l in this form is two independent parts, which are located outside an outer semi-circular arc wall b4 of the first stationary disc semi-circular arc 102 or the second stationary disc semi-circular arc 103 and are connected with a semi-circular arc wall b 4. The cover plate 101 reinforces the first stationary disk semicircle 102 or the second stationary disk semicircle 103 on the one hand, and is a connecting member of the first stationary disk semicircle 102 or the second stationary disk semicircle 103 on the other hand, and the first stationary disk semicircle 102 or the second stationary disk semicircle 103 can be directly fixed on the housing 2 or the cylinder chamber 4 through the cover plate 101. The movable plate cooperating with the fully open stationary plate is a fully closed movable plate as shown in fig. 53 and 55, in which a first circular reverse-cut plate 112 and a second circular reverse-cut plate 113 are fixed between two back plates 111. In this state, the closed air cavity ab is formed by the cooperation of the first inverse-cut circular plate 112, the first static disc semi-circular arc 102 and the two back plates; or the second inverse tangent circular plate 113 and the second stationary disc semi-circular arc 103 can be formed by matching with the two back plates together.

As shown in fig. 23, the static disc 10 may also be formed by connecting two semicircular plates b and a cover plate 101 in the axial direction, where the semicircular plates b are a first static disc semicircular arc 102 and a second static disc semicircular arc 103, and the same side in the axial direction of the first static disc semicircular arc 102 and the second static disc semicircular arc 103 is connected to one cover plate 101. The semi-open type static disc is matched with a semi-open type movable disc shown in figure 25, wherein the number of the reverse cutting circular plates a is two, and the reverse cutting circular plates are respectively a first reverse cutting circular plate 112 and a second reverse cutting circular plate 113. The first reverse cut circular plate 112 and the second reverse cut circular plate 113 are connected to a back plate 11l together on the same side in the axial direction. In this state, the closed air cavity ab is formed by the cooperation of the first inverse-cut circular plate 112 and the first stationary disc semi-circular arc 102 with the cover plate and the back plate; or the second inverse tangent circular plate 113 and the second stationary disc semi-circular arc 103 can be formed by matching the cover plate and the back plate together.

The totally enclosed static disc, as shown in fig. 59 to 62, has two cover plates 101, and a first static disc semi-circular arc 102 and a second static disc semi-circular arc 103 are fixed between the two cover plates 101. The fully-closed static disc is matched with a fully-opened movable disc shown in fig. 63 and 64, the back plate 111 is positioned between the first back-cut circular plate 112 and the second back-cut circular plate 113, and the back plate 111 is a solid structure which is formed by oppositely and centrally extending the back-cut

circular plates

112 and 113 and plays a role in connecting and fixing the back plate and the circular plate and increasing the strength. In this state, the closed air cavity ab is formed by the cooperation of the first inverse-cut circular plate 112, the first static disc semi-circular arc 102 and the two cover plates; or the second reverse cutting circular plate 113 and the second static disc semi-circular arc 103 can be formed by matching with the two cover plates together.

The cover plate 101 is a connecting piece for fixing the semicircular arc plate b, increases the strength of the semicircular arc plate b, and is usually plate-shaped or in other shapes. When the circular plate a is cut reversely and moves to do work relative to the semi-circular plate b, the semi-circular plate b can provide supporting force. The back plate 111 is a connecting piece for fixing the reverse cutting circular plate a, simultaneously the strength of the reverse cutting circular plate a is increased, the back plate is usually plate-shaped and can be in other shapes, and the back plate is driven to drive the reverse cutting circular plate a to work on the semi-circular arc plate b in the movement mode; as shown in fig. 60 and 63, the back plate 111 is a solid connection portion between two circular plates a cut reversely.

As shown in fig. 26, the movable platen 11 is provided with a bearing chamber 114. The eccentric drive mechanism cooperates with the bearing chamber 114 to drive the moving disk relative to the stationary disk. As shown in fig. 1a, the circular reverse cutting plate a is formed by connecting one end of a first semicircular plate and one end of a second semicircular plate, the opening directions of the first semicircular plate and the second semicircular plate are opposite, that is, the circular reverse cutting plate is composed of two relatively small semicircular arcs which are circumscribed and have the same diameter, the opening directions of the semicircular arcs are 180 degrees, and the whole circular reverse cutting plate is similar to a transverse S shape. The reverse cutting circular plate is short for double external reverse cutting semicircular arcs. The diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, specifically, the diameter of the inner wall at the opening of the first semicircular plate, i.e., the first outer semicircle a5, is collinear with the diameter of the inner wall at the opening of the second semicircular plate, i.e., the second inner semicircle wall a 2. The diameter of the first semicircular plate is larger than or equal to that of the second semicircular plate. As shown in fig. 9a, the center of the back plate 111 connecting the circular plate a is the back plate center o2, and the axis of the back plate center o2 is the back plate axis. The axis of the output shaft of the motor 9 is called a center line, the center line is parallel to the axis of the back plate, the center of the semicircular arc plate b is perpendicular to the center line, and the intersection point of the center line and the center line is called a cover plate center o 1. The back plate 111 and the cover plate 101 are in eccentric rotary translation, and the motion mode is as follows: the axis of the back plate revolves around the central line, the revolution radius is the distance between the axis of the back plate and the central line, the back plate 111 is provided with a device for preventing the movable disc from rotating, and the opening direction of the first semicircular plate and the opening direction of the second semicircular plate are unchanged in the process that the back plate 111 can drive the opposite-cutting circular plate a to move relative to the semicircular plate b through the device for preventing the movable disc from rotating. As shown in fig. 19b, the means for preventing the rotation of the moving disk is usually provided between the back plate 111 and the chassis of the cylinder chamber 4. The volume of the air cavity ab can be changed by moving the opposite cutting circular plate a relative to the half circular plate b; the static disc 10 is provided with an exhaust hole 107, and the inner cavity of the semi-arc plate b is communicated with the exhaust connecting pipe 29 through the exhaust hole 107.

As shown in fig. 9 a-14, the midline is drawn as the deck center o1 and the backplate axis is drawn as the backplate center o 2. The back plate 111 moves relative to the cover plate 101 in the following manner: the axis of the back plate revolves around the midline, and the revolution radius is the distance between the axis of the back plate and the midline and is also called eccentricity. When the back plate 111 drives the inverse-cut circular plate a to move relative to the semicircular plate b, the opening directions of the first semicircular plate and the second semicircular plate are unchanged, and the volume of the air cavity ab can be changed by the movement of the inverse-cut circular plate a relative to the semicircular plate b; the cover plate or the semi-arc plate b is provided with an exhaust hole. Since the back plate axis revolves around the centerline, the movement of the back plate 111 relative to the cover plate 101 will be referred to as the revolution of the back plate 111 relative to the cover plate 101 for simplicity of description.

As shown in fig. 1a, the first semicircular plate has three side surfaces, which are a first inner semicircular wall a1, a fourth end semicircular wall a4 and a first outer semicircular wall a5, respectively; the second semicircular plate has three sides, which are a second inner semicircular wall a2, a third end semicircular wall a3, and a second outer semicircular wall a6, respectively. The first inner semicircular wall a1 is connected to and tangent to the second inner semicircular wall a2, and the first outer semicircular wall a5 is connected to and tangent to the second outer semicircular wall a 6; the curved surface formed by the first outer semicircle a5 and the second outer semicircle a6 is parallel to the curved surface formed by the first inner semicircle wall a1 and the second inner semicircle wall a 2; two ends of the third end semicircular wall a3 are respectively connected with two ends of the second inner semicircular wall a2 and the second outer semicircular wall a6, and two ends of the fourth end semicircular wall a4 are respectively connected with two ends of the first inner semicircular wall a1 and the first outer semicircular wall a 5.

The side wall of the semicircular arc plate b is provided with an inner semicircular arc wall b1, an outer semicircular arc wall b4, a second end semicircular arc wall b2 and a first end semicircular arc wall b3, the inner semicircular arc wall b1 is parallel to the outer semicircular arc wall b4, one end of the inner semicircular arc wall b1 and one end of the outer semicircular arc wall b4 are respectively connected with the second end semicircular arc wall b2, the other end of the inner semicircular arc wall b1 and the other end of the outer semicircular arc wall b4 are respectively connected with the first end semicircular arc wall b3, and the diameters of the second end semicircular arc wall b2 and the first end semicircular arc wall b3 are the thickness of the semicircular arc plate b.

The sum of the diameters of the first and second inner semicircular walls a1 and a2 is equal to the sum of the diameters of the inner semicircular arc wall bl and the second end semicircular arc wall b 2.

The diameter of the second inner semicircular wall a2 minus the thickness of the semicircular arc plate b is equal to the revolution diameter of the movable plate 11 when revolving relative to the stationary plate 10. The thickness of the semicircular arc plate b is equal to the diameter of b2 or b 3. The size relation can ensure that when the reverse cutting circular plate a of the movable disc translates relative to the semicircular arc plate b of the static disc according to the set eccentricity, the first semicircular wall a1 is tangent to the semicircular arc plate b, meanwhile, the second semicircular wall a2 is tangent to the second end semicircular arc wall b2, a relatively closed air cavity ab can be formed between the semicircular arc plate b and the inner wall of the reverse cutting circular plate a, and the distance between two tangent points changes periodically from large to small or from small to large along with the revolution motion of the movable disc, so that the volume of the space of the air cylinder also changes periodically.

As shown in fig. 23, two semicircular arc plates b are disposed on the same side of the cover plate 101, one of the two semicircular arc plates is referred to as a first stationary disc semicircular arc 102, the other semicircular arc plate b is referred to as a second stationary disc semicircular arc 103, the first stationary disc semicircular arc 102 and the second stationary disc semicircular arc 103 are uniformly distributed on the concentric circle of the cover plate 101, and one axial end of the first stationary disc semicircular arc 102 and one axial end of the second stationary disc semicircular arc 103 are fixedly connected to the same side of the cover plate 101, that is, the first stationary disc semicircular arc 102 and the second stationary disc semicircular arc 103 are point-symmetric with respect to the cover plate center o1, and the axial heights of the first stationary disc semicircular arc 102 and the second stationary disc semicircular arc 103 are the same. As shown in fig. 25, two circular reverse-cut plates a are uniformly distributed in the circumferential direction around the center of one side surface of the back plate 11l, the two circular reverse-cut plates a are respectively called a first circular reverse-cut plate 112 and a second circular reverse-cut plate 113, the first circular reverse-cut plate 112 and the second circular reverse-cut plate 113 are centrosymmetric with respect to a back plate center o2, and one axial end of the first circular reverse-cut plate 112 and one axial end of the second circular reverse-cut plate 113 are fixedly connected to the same side surface of the back plate 111; the first reverse cutting circular plate 112 and the first static disc semi-circular arc 102 are matched to form a cylinder circular arc structure, and the second reverse cutting circular plate 113 and the second static disc semi-circular arc 103 form another cylinder circular arc structure. Two exhaust holes 107 are formed in the position, close to the compression end point, in the cylinder compression cavity on the static disc 10, and the forming mode of the two exhaust holes 107 is as follows: two exhaust holes 107 are axially formed in the cover plate 101, or one exhaust hole 107 is radially formed in each of the side walls of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103; the two exhaust holes 107 are respectively communicated with the inner cavities of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 in a one-to-one correspondence mode. The cover plate 101 and the back plate 111 may be both circular plates. The inner cavity of the first stationary disc semi-circular arc 102 and the inner cavity of the second stationary disc semi-circular arc 103 are respectively communicated with an exhaust channel formed by an exhaust hole 107 and an exhaust connecting pipe 29 and the outside.

As shown in fig. 9a, the distance between the midpoints of the two first inner semicircular walls a1 is a semicircular midpoint connecting line H1, i.e., a connecting line between the midpoint of the first inner semicircular wall a1 of the first inverse-tangent circular plate 112 and the midpoint of the first inner semicircular wall a1 of the second inverse-tangent circular plate 113 is referred to as a semicircular midpoint connecting line H1. The distance between the midpoints of the inner semicircular arc walls b1 of the two semicircular arc plates b is a semicircular arc midpoint connecting line H2, namely, a connecting line between the midpoint of the inner semicircular arc wall b1 of the first static disc semicircular arc 102 and the midpoint of the inner semicircular arc wall b1 of the second static disc semicircular arc 103 is called a semicircular arc midpoint connecting line H2. A connecting line H1 of the semicircular midpoints is parallel to a connecting line H2 of the semicircular midpoints, the connecting line of two end points of the semicircular arc plate b is the width L1, and a connecting line H1 of the semicircular midpoints and a connecting line H2 of the semicircular arc midpoints are perpendicular to a connecting line L1 of the two end points of the semicircular arc plate b.

The semi-arc midpoint connecting line H2 is equal to: the half-circle having its midpoint connected to line H1 plus a second inner half-circle wall a2The diameter is subtracted by the diameter of the second end semicircular arc wall b 2. Namely: h2 ═ H1+ Φ_a2-Φ_b2. The size relationship is an important guarantee that the moving disc arc and the static disc arc are theoretically tangent without friction when translating according to the set eccentricity.

The semicircular midpoint connecting line H1 is equal to or greater than the sum of the diameters of the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a 3. Namely: h1 is not less than phi_a1+Φ_a2+Φ_a3. The size relation not only can ensure a smaller distance between the two circular reverse cutting plates a of the circular arc of the movable disc, but also can consider the structural avoidance of interference between the two circular reverse cutting plates a; meanwhile, the minimum reasonable distance between the end part of the movable disc back-cut circular plate a and the end part of the static disc semi-circular plate b is also considered, so that the smoothness of an air inlet channel is ensured.

The axial height of the first inverse cutting circular plate 112 and the second inverse cutting circular plate 113 of the movable disc 11 is equal to the axial height of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 of the static disc 10, the movable disc 11 and the static disc 10 are both in dynamic clearance fit in the axial and radial directions, and the fit clearance of the tangent points of the axial and radial circular arcs is less than 0.1 mm.

As shown in fig. 19b, the housing 2 may be composed of an upper end cap 22, a cylinder 21, and a lower end cap 23. The upper end cap 22, the cylinder 21 and the lower end cap 23 are usually welded together after the internal components are assembled and fixed, but may be flanged in a mainframe. The upper end of the cylinder 21 is connected with the upper end cover 22, and the lower end is connected with the lower end cover 23. The cylinder wall of the cylinder 21 is provided with an air inlet connecting pipe 24, a liquid supplementing port 26 and a motor junction box 20 which penetrate through the cylinder wall, and the upper end cover 22 is provided with an exhaust connecting pipe 29. The lower end cover is preferably an elliptical end socket, the radial direction of the lower end cover and the cylinder body 21 are concentric circles, a fixed support 25 can be arranged outside the bottom of the lower end cover, and an oil pump body is arranged in the center of the inner part of the bottom of the lower end cover; the upper end cover 22 is preferably an elliptical end cover, and is radially concentric with the cylinder 21. The air inlet connecting pipe 24 and the fluid infusion port 26 are respectively connected with the liquid storage device 05 through pipelines, and an air inlet 051 of the liquid storage device 05 is communicated with the air inlet connecting pipe 24 of the compressor in the liquid storage device.

As shown in fig. 26, the bearing chamber 114 is located at the center portion of the back plate 111. The bearing chamber 114 is provided with an annular cavity 115 at the periphery, and the bearing chamber 114 is correspondingly concentric with the annular cavity 115. As shown in fig. 37, the eccentric driving mechanism may be composed of a main shaft 3 and a crankshaft pin 34, the crankshaft pin 34 is provided at the end of the main shaft 3, and the crankshaft pin 34 is engaged with the bearing chamber 114. As shown in fig. 30 to 32, to smooth the operation of the eccentric drive, the crankshaft 34 is fitted with a mass balance 5. As shown in fig. 33, the mass balance 5 has a connecting disc 53, a crankshaft sleeve 52 is provided in the middle of the connecting disc 53, a mounting hole 51 is provided in the crankshaft sleeve 52, an arc-shaped balance 50 is provided on the connecting disc 53, and the balance 50 is located on the periphery of the crankshaft sleeve 52. During installation, the crankshaft pin 34 is located in the mounting hole 51, the crankshaft pin sleeve 52 is located in the bearing chamber 114, and the counterweight 50 is located in the annular cavity 115. The crankshaft pin sleeve 52 can be externally provided with a bearing bush. The first and second circular reverse-

cut plates

112 and 113 are respectively located at both sides of the bearing chamber 114, and the first and second circular reverse-

cut plates

112 and 113 are centrosymmetric with respect to the center of the circle of the bearing chamber 114. A device for preventing the movable disc from rotating is arranged between the movable disc 11 and the chassis 43. The back plate 111 is provided with a key groove 117, the chassis 43 of the cylinder chamber 4 is provided with a sliding groove 41, the sliding groove 41 is positioned below the key groove 117, and the two are perpendicular to each other. The lower part of the back plate 111 is provided with a cross slip ring 8; the oldham ring 8 is constituted by a ring main body 81, an upper slide key 82, and a lower slide key 83. An upper sliding key 82 and a lower sliding key 83 are arranged on the sliding ring main body 81, the upper sliding key 82 and the lower sliding key 83 are separated by 90 degrees, and the upper sliding key 82 of the cross sliding ring 8 is in sliding fit with the key groove 117; the lower sliding key 83 of the cross sliding ring 8 is in sliding fit with the sliding chute 41; the cross slip ring 8, the sliding groove 41 and the key groove 117 are matched to form a device for preventing the rotating disc from rotating.

The eccentric driving mechanism can also be a second scheme as shown in fig. 29, the eccentric driving mechanism is composed of a main shaft 3 and a main shaft eccentric circle 32, and the main shaft 3 is provided with the main shaft eccentric circle 32. The spindle eccentric 32 cooperates with a bearing chamber 114 of the cylinder cam plate. The spindle 3 is provided with a spindle eccentricity 32, and thus such a spindle may be referred to as an eccentricity spindle. A main bearing 33 may be installed between the main shaft eccentric 32 and the bearing housing 114 to reduce friction therebetween. In the eccentric circle spindle scheme provided with the spindle eccentric circle 32, as shown in fig. 74 to 77, an upper bearing chamber 109 may be opened at the middle of the cover plate 101 in order to stabilize the operation of the spindle 3. The bearing chamber 114 is a through hole that extends axially through the rotor plate. The upper bearing 31 is attached to the main shaft 3, and the upper bearing 31 is attached to the upper bearing chamber 109. The top of the cover plate 101 is axially provided with a cylindrical balance weight chamber 110, and the upper end of the balance weight chamber 110 is provided with a balance weight chamber cover 100 for sealing. The portion of the upper end of the main shaft 3 passing through the bearing chamber 114 and the upper bearing chamber 109 in this order is provided with a mass balance 5, and the mass balance 5 is located in the balance weight chamber 110.

As shown in fig. 19b, the cover plate 101 cooperates with the cylinder chamber 4 to form a closed cylinder, and the cover plate 101 is provided with an exhaust hole 107 in the axial direction. As shown in fig. 24, the cover plate 101 is further provided with an air outlet 108, a one-way exhaust valve 290 can be installed in the air outlet 108, the one-way exhaust valve 290 is communicated with the exhaust hole 107 and the exhaust connecting pipe 29, and the exhaust hole 107, the one-way exhaust valve 290 and the exhaust connecting pipe 29 form an exhaust passage.

As shown in fig. 19b, when viewed from the lower end cap 23 inside the housing 2:

the lower end of the main shaft 3 is inserted into the center of an oil pump body to be connected with a pump wheel to run in a matching mode, then the lower end of the main shaft is matched and penetrates through a lower bearing 211 arranged in the middle of a lower support 210 upwards, then the lower bearing is connected and fixed upwards and penetrates through a rotor of a motor 9, then the lower bearing is matched and supported upwards with a main bearing 33 arranged in the center of a cylinder chamber 4 and then penetrates through a cross sliding ring 8 upwards, a mass balance block 5 is arranged on a crankshaft 34 at the upper end of the main shaft 3, and the shaft diameter of the balance block 5 is matched and connected with the middle of a movable disc 11 through a bearing or a bearing bush. The static disc 10 is installed on the upper portion of the movable disc 11 in a dynamic fit manner, as shown in fig. 24, two axial cylinder exhaust holes 107 are formed in the cover plate 101 of the static disc 10, and a one-way exhaust valve 290 is installed corresponding to the exhaust holes 107. The gas is firstly sucked from the gas inlet connecting pipe 24 of the cylinder 21 provided with the motor 9, then enters the cylinder 1 through the gas inlet 42 on the chassis 43 of the cylinder chamber 4, and then the compressed high-pressure gas is discharged into a space formed by the cover plate 101 and the end socket of the upper end cover 22 through the gas outlet valve 290, namely the high-pressure gas chamber is buffered and temporarily stored, and finally is discharged through the gas outlet connecting pipe 29 of the upper end cover 22.

As shown in fig. 19b, the lower bracket 210 in the housing 2 is fixedly connected to the lower portion of the cylinder 21, and a reasonable distance is maintained between the upper portion and the motor stator axially; the motor stator is fixedly connected with the inner wall of the shell barrel, and the upper end of the motor stator keeps a reasonable distance from the cylinder chamber 4; the cylinder chamber 4 is fixedly connected with the cylinder body 21 in the circumferential direction; the cylinder chamber wall 40 extending upwards in the axial direction of the cylinder chamber 4 is fixedly connected or matched with the cover plate 101 for floating connection; the cover plate 101, the cylinder chamber 4, the cylinder 21, the motor 9, the lower bracket 210, the oil pump impeller or gear pump driving gear and the main shaft 3 are all axially concentric.

As shown in fig. 37 to 41, the lower end of the main shaft 3 is connected with an oil pump turbine, the crankshaft pin 34 at the upper end is provided with a mass balance block 5, and the mass balance block 5 is matched with the crankshaft pin 34 through a central mounting hole 51; the center of the main shaft 3 is provided with an oil hole 35 from bottom to top for conveying lubricant from a bottom oil pool to an upper lubricating part through an oil pump during rotation.

Obviously, the main technical characteristic of the invention is that the semicircular arc cylinder is used, and other translation structures, moving parts and lubricating modes are the same as those of the existing scroll compressor.

Fig. 79 to 90 show a third embodiment of a semi-arc air conditioner compressor.

As shown in fig. 89 or fig. 90, the cylinder chamber 4 may be provided with two layers of cylinder chamber walls 40, and the two layers of cylinder chamber walls 40 may be formed as a single body or may be formed as separate bodies. One cylinder 1 is arranged in each layer of cylinder chamber wall 40, and the two cylinders 1 are sequentially arranged along the axial direction. Of course, in the scheme of arranging the upper and lower layers of cylinders 1, the cylinder chamber 4 may be completely provided with only one layer of cylinder chamber wall 40, at this time, the cover plate 101 of the lower layer of cylinders 1 is fixedly connected with the upper end of the cylinder chamber wall 40, and the cover plate 101 of the upper layer of cylinders 1 may be directly fixedly connected with the housing 2. The bearing chambers 114 of the two movable disks 11 are through holes axially penetrating through the movable disks, and as shown in fig. 87, the shaft holes 104 are formed in the middle parts of the lower cover plates 101. The air intake and exhaust of the two cylinders 1 have two design modes:

the first method is as follows: as shown in fig. 87, the cover plate 101 of the lower layer is provided with at least one air inlet 42 located outside the shaft hole 104, and the chassis 43 is provided with another air inlet 42 in the axial direction. Further, the air cavity of the lower cover plate and the blank of the chute are provided with axial air inlets 42, so that the upper air cylinder 1 is communicated with the lower air cylinder 1 through the air inlets 42 on the lower cover plate 101, at the moment, the upper and lower air cylinders 1 can share one air inlet connecting pipe 24 for air inlet, and the shell 2 is only communicated with one air inlet connecting pipe 24 with the whole air cylinder chamber, that is, only one air inlet connecting pipe 24 can be arranged on the shell 2.

As shown in fig. 82, two air outlet holes 108 are axially formed in the cover plate 101 of the upper cylinder 1, and two air outlet holes 108 are radially formed in the cylinder chamber wall 40 of the lower cylinder. Two exhaust holes 107 are axially formed in the cover plate 101 of the upper layer of the cylinder 1, one exhaust hole 107 is radially formed in each of the side walls of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 of the lower layer of the cylinder 1, and the two air outlet holes 108 on the same layer are respectively communicated with the two exhaust holes 107 of the corresponding cylinder 1 in a one-to-one correspondence manner. The top of the upper end cover 22 is provided with an exhaust connecting pipe 29, and two air outlet holes 108 on the upper layer are directly communicated with the inner cavity of the upper end cover 22 through a one-way valve. As shown in fig. 77 and 78, the two air outlets 108 on the lower layer are respectively communicated with the inner cavity of the upper end cap 22 through a one-way valve and a communicating pipe 291, and the design enables the exhaust air to be uniformly exhausted through an exhaust connecting pipe 29 after being buffered by the inner cavity of the upper end cap 22, thereby ensuring the smooth air supply to the condenser 02. The two air inlets 42 are axially communicated, the air inlet connecting pipe 24 is communicated with the air inlet 42 axially arranged on the base plate 43, and the design only has one air inlet connecting pipe 24, so that the volume of the air-conditioning compressor is smaller, and the internal structure is more compact. In this embodiment, the upper bearing 31 may be attached to the main shaft 3, and the upper bearing 31 may be attached to the upper bearing chamber 109. The top of the cover plate 101 is axially provided with a cylindrical balance weight chamber 110, and the upper end of the balance weight chamber 110 is provided with a balance weight chamber cover 100 for sealing. The upper end of the main shaft 3 passes through the bearing chamber 114 and the upper bearing 31 of the upper bearing chamber 109 in sequence, and the end part thereof is provided with the mass balance 5, and the mass balance 5 is positioned in the balance weight chamber 110.

The second method comprises the following steps: as shown in fig. 90, at least one air inlet 42 is radially formed in the upper cylinder chamber wall 40, and at least one air inlet 42 is axially formed in the base plate 43. Two air outlet holes 108 are radially formed in the wall 40 of each layer of the cylinder chamber, and an exhaust hole 107 is radially formed in each of the side walls of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103. The two air outlet holes 108 on the same layer are respectively communicated with the air outlet holes 107 of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 on the same layer, so as to be communicated with the inner cavity of the first static disc semi-circular arc 102 and the inner cavity of the second static disc semi-circular arc 103. Four exhaust connecting pipes 29 are arranged on the shell 2, and the four exhaust connecting pipes 29 are communicated with four air outlet holes 108 in a one-to-one correspondence manner. The inner cavity of the first stationary disk semicircle 102 or the inner cavity of the second stationary disk semicircle 103 may communicate with the air inlet of the condenser 02 through an exhaust passage formed by the exhaust hole 107, the exhaust hole 108 and the exhaust connection 29. Two air inlet connecting pipes 24 are arranged on the side wall of the shell 2, and the two air inlet connecting pipes 24 are communicated with the two air inlets 42 in a one-to-one correspondence manner. The specific opening positions of the air inlets 42 on the upper layer and the lower layer are shown in fig. 90, one air inlet 42 can be radially opened on the cylinder chamber wall 40 on the upper layer, and the air inlet 42 can be axially opened on the base plate 43. In the above solution, if the cylinder chamber 4 is provided with only one layer of cylinder chamber wall 40, the housing 2 corresponding to the upper layer of cylinders 1 is provided with an air inlet 42 in the radial direction to supply air to the upper layer of cylinders 1. Similarly, because there is no upper cylinder chamber wall 40, the two exhaust holes 107 of the upper cylinder can be directly communicated with the two upper exhaust connecting pipes 29 on the upper layer of the housing 2 in a one-to-one correspondence manner, and the inner cavity of the first stationary disk semi-circular arc 102 or the second stationary disk semi-circular arc 103 of the upper cylinder 1 can be communicated with the air inlet of the condenser 02 through the exhaust passage formed by the exhaust holes 107 and the exhaust connecting pipes 29.

In order to prevent liquid from entering the cylinder and avoid liquid impact, as shown in fig. 19 and 66, and fig. 77 and 78, an existing reservoir 05 can be installed outside the air inlet connection tube 24, and a liquid outlet of the reservoir 05 is communicated with the liquid replenishing port 26 of the housing 2 through a pipeline.

The eccentric driving mechanism can be composed of a main shaft 3 and two main shaft eccentric circles 32, and the two main shaft eccentric circles 32 are axially arranged on the main shaft 3. The two main shaft eccentrics 32 each cooperate with a bearing chamber 114 of one cylinder 1. In order to enable the main shaft 3 to pass through the lower cylinder 1 to be matched with the bearing chamber 114 of the upper cylinder 1, a through hole with enough size needs to be reserved in the middle of the movable disc 11 and the static disc 10 of the lower cylinder 1. The bottom of each cylinder 1 is respectively provided with a set of device for preventing the rotation of the movable disc, the upper chute 41 for preventing the rotation of the movable disc is arranged on the cover plate 101 of the cylinder 1 below, and the lower chute 41 for preventing the rotation of the movable disc is arranged on the chassis 43.

The two main shaft eccentric circles 32 are axially arranged in sequence, are radially symmetrical about the main shaft axis by 180 degrees, and are respectively matched with the bearing chamber 114 of one cylinder 1.

The number of the main shaft eccentric circles 32 may be two, three, four or more, and the number of the main shaft eccentric circles 32 is the same as the number of the bearing chambers 114. Alternatively, all the spindle eccentric circles 32 are arranged axially in sequence and are uniformly distributed in the circumferential direction of the spindle 3, for example, when there are two spindle eccentric circles 32, the spatial angle is 180 degrees, when there are three spindle eccentric circles 32, the spatial angle is 120 degrees, and so on.

According to the axial multilayer compressor scheme, a compressor scheme with three or more layers can be designed. If the compressor is a three-layer compressor, the axial dimension of the cylinder arc structure of the middle layer cylinder is two times of the axial dimension of the cylinder arc structures of the upper layer and the lower layer at the two axial sides, and the mass of the middle layer movable disc is two times of the mass of the upper layer movable disc and the lower layer at the two axial sides; the eccentric circular mass centers of the main shafts on the upper layer and the lower layer on the two sides are symmetrical about the mass center of the movable disc in the middle layer in the axial direction; in the radial direction, the eccentric circle of the main shaft in the middle layer is circumferentially symmetrical with the coaxial eccentric circles on two sides in the axial direction by 180 degrees of the axis of the main shaft. The balance of the moving mass of the compressor with the three cylinders in the radial direction and the axial direction can realize natural balance, namely, the technical scheme directly solves the balance problem in design without additionally increasing a balance device. The centrifugal force of the radial cylinder and the eccentric circle is balanced, and the sum of the stress and the mass of the two ends in the axial direction is equal to that of the middle layer, so that the balance is achieved.

As shown in fig. 61a to 61f, each of the static discs 10 is composed of two parts, one part is provided with a first static disc semi-circular arc 102, and the other part is provided with a second static disc semi-circular arc 103. The static disc 10 is divided into two parts to be processed and manufactured respectively, the processing difficulty and the cost are lower, and meanwhile, the structure in the static disc is easier to install and overhaul for the embodiment of the multilayer cylinder.

Further description is as follows:

firstly, the main operating principle of the cylinder 1 is as follows: the back plate revolves around the center of the cover plate, so that the inverse cutting circular plate is driven to move along the semicircular arc plate. In addition, in the moving process of the circular arc plate and the semicircular arc plate, the motion conditions of each point on the circular arc plate are completely the same, so that the relative motion between the circular arc plate and the semicircular arc plate is translation. In the revolution process, the circular plate a and the semicircular plate b can form a relative closed space together with the cover plate and the back plate at the two ends of the height of the circular plate a and the semicircular plate b, the relative closed space is called as an air cavity, and the volume of the air cavity can be gradually changed from large to small along with the revolution. In theory, the volume of the entire air cavity can be compressed from the initial nominal design value all the way to zero, which is close to the extreme value. During the process, the cylinder compression cavity formed by the semi-circular arc and the circular plate is in extremely small clearance fit at the radial closed point ab of the air cavity, and no contact friction exists. Meanwhile, the clearance between the two is extremely small and is less than 0.1mm, so the leakage amount is also very small, namely the volume efficiency is higher. Optionally, in a high-pressure machine type requiring high sealing, a sealing element can be arranged in the axial direction of the arc, a floating structure can be adopted in the radial direction and the axial direction, and the sealing effect can meet the design requirement.

In operation of the cylinder, as shown in fig. 3 to 7, the first inner semicircular wall a1 of the circular plate a can be tangent to the inner semicircular arc wall b1 of the semicircular plate b in a 180 ° translational range, forming a tangent point on the drawing; the second inner semicircular wall a2 may be tangent to a line at one end semicircle of the semicircular plate b within 180 ° to form another tangent point on the drawing, and as shown in fig. 15 and 16, the tangent point will move relatively in the moving state: when the translation direction is towards the second inner semicircular wall a2, the two tangent points are gradually close, and the space volume formed by the semicircular arc plate b, the circular plate a and the cover plate back plates at the two ends in the height direction is reduced until the space volume is close to zero of an extreme value. On the contrary, the distance between the two tangent points is gradually enlarged, and the volume is changed from the minimum value to the maximum value. Since this cylinder is used for compression, it is provided that the translational direction of the moving disk is always directed towards the second inner semicircular wall a2 during the compression of the gas. When the volume of the air cavity formed by the semicircular arc plate b and the reverse cutting circular plate a is compressed, the volume of the space at the open end of the semicircular arc plate b is synchronously enlarged and air is synchronously sucked. Therefore, the cylinder exhaust port of the present invention is disposed at a position close to the volume compression end point in the semicircular plate b, and may be radially disposed to penetrate through the semicircular plate b, or may be axially disposed to penetrate through the cover plate 101 in the height direction of the circular arc.

Because the air cylinder scheme can only do work within 180 degrees in the translation process of the movable disc during operation, and the other 180-degree rotary radius is only used for the rotary motion of the movable disc without doing work, the invention can adopt a double-air cylinder arrangement scheme in order to improve the power density.

In the double-cylinder arrangement scheme, as shown in fig. 8 to 14, the circular plates a of the two cylinder structures can be manufactured into a whole, and the two semicircular plates b are respectively connected and fixed with the shell or the bracket into a whole or directly manufactured into a whole and then connected with the shell or the bracket. Thus, when one cylinder does work, the other cylinder rotates; when the other cylinder does work, the cylinder which does work in front starts the rotation process, and the whole compressor continuously works in a 360-degree rotation range in a cycle.

As shown in fig. 23, the outer semicircular arc wall 103b4 of the second stationary disc semicircular arc is integrally connected with the reinforcing metal structure, so that the outer circular arc line of the outer semicircular arc wall 103b4 of the second stationary disc semicircular arc is hidden in the machine body extending from the outer circle of the stationary disc circular arc. The end part of the semicircular arc plate is semicircular. The diameter of the end part of the semicircular arc plate is equal to the radial thickness of the arc. As shown in FIG. 9a, the maximum center distance H2 between the inner circles of the two semicircular arc plates of the static disc is equal to the maximum center distance H1 between the outer circles of the circular plate cut reversely by the movable disc plus the revolution diameter of the movable disc during operation. The revolution diameter is twice the eccentricity. The axial height of the two circular arc plates of the static disc is equal to the axial height of the circular plate reversely cut by the movable disc, so that the static disc and the movable disc can be matched to form a sealed air cavity. The one end and the apron of quiet dish semicircle board height are connected, and the other end is opened, and whole quiet dish cylinder volume part is semi-open.

The back plate is circular, and two circular plates which are reversely cut are uniformly distributed on a circle taking the circle center of the back plate as the circle center. The eccentricity is the revolution distance between the circle center of the back plate and the circle center of the cover plate. As shown in fig. 25, the non-meshing arc surfaces of the two circular reverse cutting plates and the semi-circular arc plate of the stationary disc are respectively connected with the metal reinforced connecting structure into a whole, i.e. the two circular reverse cutting plates are physically connected, i.e. the first outer semi-circular a5 and the second outer semi-circular a6 are integrally connected with the metal reinforced connecting structure, so that the arc surfaces of the non-meshing surfaces of the circular reverse cutting plates are integratedHidden in the moving disc arc machine body. The end part of the reverse cutting circular plate is semicircular. The diameter of the end part of the reverse cutting circular plate is equal to the radial thickness of the circular arc. The maximum circular arc center distance H1 between the two circular arc plates facing the inner circle of the semi-circular plate of the static disc is larger than or equal to the sum of the diameters of the first inner semi-circular wall a1, the second inner semi-circular wall a2 and the third end semi-circular wall a3 which form the circular arc plate a of the circular arc plates of the reverse cutting, namely the center distance H1 is more than or equal to phi_a1+Φ_a2+Φ_a3It is apparent that the sum of the diameters of the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a3 is equal to the sum of the diameters of the first end semicircular wall a4, the second outer semicircular wall a5 and the third outer semicircular wall a6, i.e. phi_a1+Φ_a2+Φ_a3＝Φ_a4+Φ_a5+Φ_a6. And one end of the height of the reverse cutting circular plate a is connected with the back plate, and the other end of the reverse cutting circular plate a is opened, so that the volume part of the cylinder of the movable disc becomes a half-open form.

The axial opening parts of the movable disc and the static disc are buckled together, and are in axial and radial clearance fit, because the heights of the circular plate reversely cut by the movable disc and the semi-circular arc plate of the static disc are the same, the two ends of the circular plate are sealed by the cover plate and the back plate, and the arc volume formed in the radial direction is sealed by two tangent points changed in the translation, so that a relatively sealed air cavity ab is formed, and the space volume of the air cavity ab can be changed circularly, so that the processes of air suction, compression and exhaust are realized during operation. The exhaust port is arranged at the end position close to the arc compression of the static disc, radial exhaust is performed if the exhaust port is radially arranged on the side wall of the semicircular arc plate, and axial exhaust is performed if the exhaust port is arranged on the cover plate. The rotation preventing device is not limited to a cross slip ring scheme, other existing mechanisms with the same function can be adopted, for example, a plurality of parallel small crankshaft structures can be adopted, one or more small crankshafts parallel to the main shaft in the axial direction can be connected to one side face of the back plate in a matched mode, the other ends of the small crankshafts are installed on the bottom plate or the static plate in a matched mode, the small crankshaft slightly deviates from the axis of the small crankshafts and equals to the eccentricity of the main shaft, the small crankshaft and related bearing parts and the like can form a movable plate to prevent the self-transmission mechanism, and the small crankshaft can be arranged in a conventional mode and are not detailed. But the cross slip ring scheme is simplest and the processing cost is lowest. The center of the cover plate can be provided with a through main shaft through hole or not, whether the through main shaft through hole is arranged or not is mainly determined by whether the main shaft of the translation mechanism penetrates through the static disc or not, and the technical personnel can flexibly determine according to the actual situation.

As shown in fig. 47 to 56, the movable plate is completely enclosed at both axial ends, i.e. both axial ends are respectively provided with a back plate with the same size, at this time, the corresponding stationary plate is only provided with a semicircular arc plate and a supporting and fixing connection part thereof, and both axial ends are not provided with a cover plate. The cylinder driving disk undercut circular plate of this scheme is because the axial both ends all have the backplate fixed, and intensity is high, nevertheless can lead to the driving disk motion quality to strengthen, leads to quiet dish semicircle board simultaneously because there is not the fixed stability variation of axial tip apron.

As shown in fig. 59 and 62, the stationary disc of the cylinder may also be a disc whose two axial ends are totally closed, that is, two axial ends are respectively connected and fixed by a cover plate with the same size, a through hole for the main shaft to pass through and move is reserved in the middle of the cover plate, and the corresponding circular plate with the movable disc reverse cutting is a full open type, that is, there is no back plate at the two axial ends of the circular plate with the movable disc reverse cutting, and only the circular plate with the reverse cutting and the middle connection fixing structure and the shaft hole are provided. The advantage of this kind of cylinder scheme is that the driving disk quality is light more easily to be processed, and the shortcoming is because the fixed bolster effect that loses the backplate, and driving disk backstep circular slab intensity reduces, leads to driving disk translation mechanism's the rotation preventing device setting comparatively complicated simultaneously.

The cylinder can also be a movable disc and a static disc which are all open, namely, the static disc only has an arc plate and a radial connecting and supporting part but does not have cover plates at the two axial ends, the movable disc also only has a reverse cutting circular plate, a middle connecting and fixing part and a shaft hole, and an axial back plate does not exist. The apron and the backplate of whole cylinder are made the laminating alone and are installed in driving disk and quiet axial both ends of dish, constitute cylinder enclosure volume with driving disk circular arc, quiet dish circular arc. The technical scheme has the advantages that the reverse cutting circular plate and the semicircular arc plate are easy to process, the defects that the strength of the dynamic and static arcs is lost, the fixation of the cover plate and the back plate is reduced, the stability is poor, and particularly, the anti-rotation device of the translation mechanism is not convenient to set.

The invention has the positive effects that: the cylinder operation mode and the driving mode of the semi-arc air conditioner compressor are similar to those of a scroll compressor and are both revolution driving modes. Meanwhile, the moving disc arc and the static disc arc change through tangential motion, so that the volume change of the closed space of the cylinder is achieved, and the purpose of compressing fluid is achieved. Theoretically, the movable disc and the static disc are positioned and supported in the axial direction and the radial direction, contact friction does not occur in the operation process, so the efficiency is high, and meanwhile, the compression clearance between the gap between the movable disc and the static disc of the cylinder and the volume of the cylinder is extremely small, so the clearance loss is small, and therefore the scroll compressor inherits a plurality of advantages of the scroll compressor. However, compared with a scroll compressor, the air conditioner compressor of the invention has the following advantages: the revolution matching surface of one cylinder only has two or two pairs of arc-shaped bodies, the axial sections of the matching surfaces of the arc-shaped bodies are both standard semicircles or the combination of the standard semicircles, the back plate and the cover plate can be standard whole circles or parts of the standard whole circles, the manufacturing process is simple, the mechanical processing is very easy, and further compared with a scroll compressor, the compressor disclosed by the invention has the advantages that the manufacturing process is simplified, and the manufacturing cost is greatly reduced. Meanwhile, as the process structure is simple, if the axial size or the radial size of the cylinder is increased, or the eccentricity of the movable disc is adjusted and increased, or the technical proposal is combined, the equipment load can be easily increased, so that the manufacture of the high-efficiency high-stability large-load translation compressor becomes possible.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.

Fig. 1 to 14 are schematic structural views of a cylinder of an air conditioner compressor according to the present invention, in which a back plate 111 and a cover plate 101 are omitted for convenience of explanation and understanding, and for highlighting the shapes and the fitting relationship of a circular plate a and a semi-circular plate b of a core fitting part. Wherein fig. 1 to 7 are schematic diagrams of the structure and the operation principle of the single cylinder:

fig. 1 is a front view structure diagram of a single cylinder, and fig. 2 is a three-dimensional diagram of fig. 1. Fig. 3 to 7 are schematic views showing the simulation operation of the circular arcs of the moving plate 11 and the static plate 10 of the single cylinder, wherein fig. 3 is a schematic view showing a state where a tangent point indicated by an arrow of the circular plate a is zero, and at this time, in a compression start state, the volume of the air cavity ab is maximum; fig. 4 to 7 are schematic views of the states of the tangent points at 90 °, 180 °, 270 ° and 360 °, respectively; fig. 1a is an enlarged view of fig. 1 to describe the structure of a single cylinder in detail.

Fig. 8 to 14 are schematic structural views of the double cylinder scheme, wherein fig. 8 is a three-dimensional view of the double cylinder scheme. FIG. 9 is a schematic front view of the structure of FIG. 8; FIGS. 10-14 are simulated operating schematics of the dual cylinder arrangement; fig. 9a is an enlarged schematic view of fig. 9 to illustrate structural features of the dual cylinder scheme in detail.

Fig. 15 to 18 are detailed track diagrams showing the change of the matching position of the circular reverse cutting plate a and the circular semi-circular arc plate b in a circle of revolution, and the circular reverse cutting plate a and the circular semi-circular arc plate b are tangent in fig. 15 and 16. However, the line segment is only shown as one point in the figure, so for the sake of simplicity of description, the line segment is referred to as a tangent point, and further:

fig. 15 is a movement track diagram of the opposite semicircular plate a moving from the tangent point 0 degrees to the tangent point 90 degrees, the tangent point indicated by the arrow gradually moves from the leftmost end of the inner semicircular arc wall b1 to the center along the inner semicircular arc wall b1, in the process, the first inner semicircular wall a1 is always tangent to the inner semicircular arc wall b1, and the second end semicircular arc wall b2 is always tangent to the second inner semicircular wall a 2;

fig. 16 is a diagram of a motion trajectory of the opposite semicircular plate a moving from the tangent point 90 degrees to the tangent point 180 degrees, the tangent point indicated by an arrow moving from the center of the inner semicircular arc wall b1 to the rightmost end thereof, at this time, the first inner semicircular wall al, the inner semicircular arc wall b1, the second end semicircular arc wall b2 and the second inner semicircular wall a2 are tangent to the same point together, and in this process, the first inner semicircular wall a1 and the inner semicircular arc wall b1, and the second end semicircular arc wall b2 and the second inner semicircular wall a2 are tangent all the time;

fig. 17 is a motion track diagram of the opposite semicircular arc plate a and the semicircular arc plate b moving from the tangent point of 180 degrees to the tangent point of 270 degrees, wherein the opposite circular arc plate a and the semicircular arc plate b are gradually separated from each other by tangency;

fig. 18 is a diagram showing a movement locus of the circular reverse-cut plate a moving from 270 degrees to 360 degrees from the tangent point to the semicircular arc plate b, the circular reverse-cut plate a gradually returning to the tangent point from the separation to start the next cycle.

Fig. 19 to 46 are a schematic structural diagram of the first scheme of the semi-arc air conditioner compressor and a schematic structural diagram of main components:

FIG. 19 is a three-dimensional schematic view of a first version of a semi-circular arc air conditioner compressor, FIG. 19a is a front view of the semi-circular arc air conditioner compressor, and FIG. 19b is an enlarged schematic view of FIG. 19aA-A taken in section; FIG. 20 is an enlarged three-dimensional schematic view of a cylinder in a semi-circular arc air conditioner compressor, FIG. 21 is a side view of FIG. 20, and FIG. 22 is a bottom view of FIG. 21; FIG. 23 is a three-dimensional schematic view of the stationary plate of FIG. 20, and FIG. 24 is a bottom view of FIG. 23; FIG. 25 is a schematic three-dimensional view of the cylinder manifold of FIG. 20, FIG. 26 is a three-dimensional view at an upper elevation angle of FIG. 25, FIG. 27 is a front view of FIG. 26, and FIG. 28 is a cross-sectional view taken along line 27B-B; FIG. 29 is a perspective view of an eccentric circular main shaft with a main bearing, a stationary disc bearing housing bearing and a balance weight attached thereto; FIG. 30 is a three-dimensional schematic view of a crankshaft slightly main shaft structure of a semi-circular arc air conditioner compressor with a mass balance block mounted thereon, FIG. 31 is a three-dimensional schematic view from another angle of FIG. 30, and FIG. 32 is a front view of FIG. 30; FIG. 33 is an enlarged view of the mass balancing block of FIG. 30, FIG. 34 is a three-dimensional view at an upper elevation of FIG. 33, FIG. 35 is a front view of FIG. 33, and FIG. 36 is a cross-sectional view taken along line C-C of FIG. 35; FIG. 37 is a schematic view of the principal axis of the crankshaft arrangement of FIG. 30, FIG. 38 is a schematic view of the three-dimensional arrangement of another perspective of FIG. 37, FIG. 39 is a side view of FIG. 37, FIG. 40 is a top view of FIG. 39, and FIG. 41 is a cross-sectional view taken along line D-D of FIG. 40; fig. 42 is a schematic three-dimensional structure diagram of a cross slip ring in a semi-arc air conditioner compressor.

Fig. 43 is a perspective view of the cylinder chamber 4; FIG. 44 is a top view of FIG. 43; FIG. 45 is a cross-sectional view E-E of FIG. 44; fig. 46 is a cross-sectional view F-F of fig. 45.

FIG. 47 is a schematic view showing the structure of the fully closed movable plate and the fully open stationary plate; FIG. 48 is a schematic sectional view of FIG. 47 taken at G-G; FIG. 49 is a bottom view of the structure of FIG. 47; FIG. 50 is a schematic top view of the structure of FIG. 47; FIG. 51 is a schematic perspective view of FIG. 47; FIG. 52 is a front view of the cam plate in its fully closed position; FIG. 53 is a schematic cross-sectional view H-H of FIG. 52; FIG. 54 is a top view of FIG. 52; FIG. 55 is a perspective view of FIG. 52; FIG. 56 is a bottom view of FIG. 52; FIG. 57 is a left side view of FIG. 52; FIG. 58 is a right side view of FIG. 52; FIG. 59 is a schematic view of the engagement of a fully open movable plate with a fully closed stationary plate; FIG. 60 is a cross-sectional view I-I of FIG. 59; FIG. 61 is a top view of FIG. 59; FIG. 62 is a perspective view of FIG. 59; FIG. 63 is a top plan view of the fully open cam plate; FIG. 64 is a three-dimensional view of FIG. 63;

FIG. 61a is a three-dimensional schematic view of the stationary plate divided into two parts, wherein the two parts have the same structural shape and are spliced into the stationary plate, and the two parts are symmetrical with respect to the center of the circle of the cover plate; FIG. 61b is a three-dimensional schematic view in elevation of FIG. 61a, FIG. 61c is a front view of the stationary plate, FIG. 61d is a sectional view taken along line J-J of FIG. 61c, FIG. 61e is a bottom view of FIG. 61c, and FIG. 61f is a top view of FIG. 61 c;

fig. 65 is a schematic structural view of the spindle, and two spindle eccentric circles 32 are arranged on the spindle 3;

fig. 66 to fig. 76 are a schematic structural diagram and a schematic structural diagram of main components of a second scheme of the semi-arc air conditioner compressor:

FIG. 66 is a perspective view of a second version of the semi-circular air conditioning compressor; FIG. 66a is a top view of FIG. 66; FIG. 67 is an enlarged cross-sectional structural view of K-K of FIG. 66 a; FIG. 68 is a perspective view of the cylinder shown in FIG. 67; FIG. 69 is a front view of the stationary plate of the illustrated cylinder; FIG. 70 is a top view of FIG. 69; FIG. 71 is a sectional view taken along line L-L of FIG. 70; FIG. 72 is the perspective view of FIG. 69 with the bottom of the stationary plate visible; FIG. 73 is a bottom view of FIG. 69; FIG. 74 is the perspective view of FIG. 69, with the top of the stationary plate visible; FIG. 75 is a perspective view of the cam plate shown in FIG. 68, with the bottom of the cam plate visible; FIG. 76 is a perspective view of the cam plate shown in FIG. 68, with the top of the cam plate visible;

fig. 77 to fig. 90 are a schematic structural diagram and a schematic structural diagram of main components of a third scheme of the semi-arc air conditioner compressor:

FIG. 77 is a perspective view of a third version of the semi-circular air conditioning compressor; FIG. 78 is a front view of FIG. 77; FIG. 79 is an enlarged cross-sectional view of the M-M cylinder of FIG. 78 showing two cylinders arranged axially; FIG. 80 is a perspective view of the double layer cylinder of FIG. 79; FIG. 81 is a perspective view of the double layer cylinder of FIG. 79 from another angle; FIG. 82 is a exploded view of FIG. 81, showing the upper tier having a pair of stationary and moving disks forming an upper tier cylinder and the lower tier having another pair of stationary and moving disks forming a lower tier cylinder; FIG. 83 is a front view of the stationary plate of the lower cylinder; FIG. 84 is the perspective view of FIG. 83 with the bottom surface of the stationary plate visible; FIG. 85 is a top view of FIG. 83; FIG. 86 is a cross-sectional view N-N of FIG. 85; FIG. 87 is a bottom view of FIG. 83; FIG. 88 is the perspective view of FIG. 83 showing the top surface of the stationary plate having a keyway 117; fig. 89 is a schematic view of the structure of the upper end cap 22 and the cylinder chamber 4 having two layers of cylinder chamber walls 40, in which the top of the upper end cap 22 is provided with an exhaust connection pipe 29, and the lower cylinder chamber wall 40 is provided with two radial air outlet holes 108; fig. 90 is a schematic view of the fitting structure of the upper end cap 22 and the cylinder chamber 4 having the double-layered cylinder chamber wall 40, in which the upper end cap 22 has an exhaust connection pipe 29 at its side, the upper cylinder chamber wall 40 can be provided with an air inlet 42 and two air outlet holes 108 in the radial direction, and the lower cylinder chamber wall 40 can be provided with two air outlet holes 108 in the radial direction;

fig. 91 is a system schematic of the air conditioning architecture.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be described in detail below. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the examples given herein without any inventive step, are within the scope of the present invention.

Air conditioner compressor with single cylinder

As shown in fig. 1, a cylinder 1 of an air conditioner compressor includes a stationary disc 10 and a movable disc 11. The stationary disc 10 is formed by a semicircular plate b and a cover plate in the axial direction of the semicircular plate b, and the semicircular plate b is generally perpendicular to the cover plate. The movable plate 11 is composed of a reverse cut circular plate a and a back plate in the axial direction of the reverse cut circular plate a, and the reverse cut circular plate a is perpendicular to the back plate 111. The cover plate and the back plate are generally circular disks and have the structural shapes of a protruding semicircular arc plate b and a reverse cutting circular plate a, and the cover plate and the back plate are omitted in fig. 1 to 7. The semicircular arc plate b and the circular plate a are matched between the cover plate and the back plate, and the cover plate, the back plate, the semicircular arc plate b and the circular plate a are matched together to form a relatively closed air cavity ab. The air conditioner compressor of the scheme is called a single-cylinder air conditioner compressor because the air conditioner compressor only has one air cavity ab.

The cylinder 1 is arranged in the cylinder chamber 4 to form a compressor main body, the lower part of the compressor main body is provided with the motor 9, an output shaft of the motor 9 is provided with an eccentric driving mechanism, the movable disc 11 is provided with a bearing chamber 114, and the eccentric driving mechanism is matched with the bearing chamber 114. The motor 9 drives the movable disc 11 to do eccentric rotary translation relative to the static disc 10 through an eccentric driving mechanism. The compressor body and the motor 9 are both mounted in the housing 2. The static disc 10 is provided with an exhaust hole 107, and the chassis 43 is provided with an air inlet 42. The shell 2 is provided with an air inlet connecting pipe 24 and an air outlet connecting pipe 29, the air inlet 42 is communicated with the air inlet connecting pipe 24, and the inner cavity of the semicircular arc plate b is communicated with the air outlet connecting pipe 29 through an air outlet 107.

As shown in fig. 1, the reverse cut circular plate a is formed by connecting one end of a first semicircular plate and one end of a second semicircular plate, and the opening directions of the first semicircular plate and the second semicircular plate are opposite, that is, the opening directions of the first semicircular plate and the second semicircular plate are 180 degrees. The diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, and the diameter of the first semicircular plate is larger than that of the second semicircular plate. The axial end face of the reverse cut circular plate a is similar to an S-shape. The center of the back plate is the back plate center o 2. The axis of the output shaft of the motor 9 is called a center line, the center line is parallel to the axis of the back plate, the center of the semicircular arc plate b is perpendicular to the center line, and the intersection point of the center line and the center line is called a cover plate center o 1. The axis of the back plate center o2 is the back plate axis, and the midline is parallel to the back plate axis. The back plate 111 moves relative to the cover plate 101 in the following manner: the axis of the backboard revolves around the midline, and the revolution radius is the distance between the axis of the backboard and the midline. In the process that the back plate 111 drives the inverse-cutting circular plate a to move relative to the semicircular arc plate b, the opening directions of the first semicircular plate and the second semicircular plate are always unchanged, namely, the inverse-cutting circular plate a translates or translates relative to the semicircular arc plate b. The translation of the circular plate a and the semicircular plate b can change the volume of the air cavity ab so as to complete the actions of air suction, compression and air exhaust, and the operation is circulated. During air suction, air enters the cylinder 1 through the air inlet connecting pipe 24 and the air inlet 42 in sequence. When exhausting, the high-pressure gas is exhausted out of the cylinder 1 through the exhaust hole 107 and the exhaust connecting pipe 29 from the inner cavity of the semi-arc plate b in sequence.

As shown in fig. 1a, the first semicircular plate has three side surfaces, which are a first inner semicircular wall a1, a fourth end semicircular wall a4 and a first outer semicircular wall a5, respectively. The second semicircular plate has three sides, which are a second inner semicircular wall a2, a third end semicircular wall a3, and a second outer semicircular wall a6, respectively. The first inner semicircular wall a1 is connected to and tangent to the second inner semicircular wall a2, the first outer semicircular wall a5 is connected to and tangent to the second outer semicircular wall a6, and the connection point on the end faces of the first inner semicircular wall a1 and the second inner semicircular wall a2 is also the point of tangency of the two circles on which the two are located. Since the reverse cut circular plate a has a certain thickness, the first inner semicircular wall a1 corresponds to the first outer semicircular wall a5, and the second inner semicircular wall a2 corresponds to the second outer semicircular wall a 6. The curved surfaces formed by the first outer semicircle a5 and the second outer semicircle a6 are parallel to the curved surfaces formed by the first inner semicircle wall a1 and the second inner semicircle wall a 2. Both ends of the third end semicircular wall a3 are respectively connected with both ends of the second inner semicircular wall a2 and the second outer semicircular wall a6, and both ends of the fourth end semicircular wall a4 are respectively connected with both ends of the first inner semicircular wall a1 and the first outer semicircular wall a 5. The third end semicircular wall a3 and the fourth end semicircular wall a4 are arranged to avoid the phenomenon that the strength is weakened or the service life and the sealing performance are influenced due to the peak structure at the end of the circular plate a which is cut back. Specifically, the reverse cut circular plate a has two ends of inner and outer parallel equidistant arcs, and a third-end semicircular wall a3 and a fourth-end semicircular wall a4 are arranged with the distance between the two parallel arcs as the diameter. It is apparent that the semicircular end points of the third end semicircular wall a3 are respectively connected with the corresponding semicircular end points of the second inner semicircular wall a2 and the second outer semicircular wall a6, and the semicircular end points of the fourth end semicircular wall a4 are respectively connected with the corresponding end points of the first inner semicircular wall a1 and the first outer semicircular wall a 5.

As shown in fig. 1a, the side wall of the semicircular arc plate b has an inner semicircular arc wall b1, an outer semicircular arc wall b4, a second end semicircular arc wall b2 and a first end semicircular arc wall b 3. Inner semi-circular arc wall b1 and outer semi-circular arc wall b4 equidistance form, and the one end of inner semi-circular arc wall b1 and the one end of outer semi-circular arc wall b4 are connected with second end semi-circular arc wall b2 respectively, and the other end of inner semi-circular arc wall b1 and the other end of outer semi-circular arc wall b4 are connected with first end semi-circular arc wall b3 respectively, and the diameter of second end semi-circular arc wall b2 and first end semi-circular arc wall b3 is the thickness of semi-circular arc board b. The thickness of the semicircular arc plate b can be equal to or different from the arc thickness of the reverse cutting circular plate a, and the specific situation is determined according to the strength design and the technical characteristics of the cylinder scheme of the invention.

As shown in fig. 1a, the sum of the diameters of the first and second inner semicircular walls a1 and a2 is equal to the sum of the diameters of the inner semicircular arc wall b1 and the second end semicircular arc wall b 2. That is, as can be seen from fig. 1a, the sum of the diameters of the first inner semicircular wall a1 and the second inner semicircular wall a2 in the circular arc-shaped plate a is referred to as the mating surface diameter of the circular arc-shaped plate a, and the sum of the diameters of the inner semicircular wall b1 and the second end semicircular wall b2 in the circular arc-shaped plate b is referred to as the arc mating surface diameter of the circular arc-shaped plate b.

As shown in fig. 1, the radius of the second inner semicircular wall a2 minus the radius of the second end semicircular arc b2 is equal to the revolution radius of the movable plate 11 when revolving relative to the stationary plate 10. The size relationship determines the matching and sealing of the second end semicircular arc wall b2 end of the cylinder cavity in the revolution process of the movable and static discs.

The operation principle of the semi-arc air conditioner compressor is described in detail below with reference to fig. 3 to 7.

The motor 9 drives the movable disc 11 to move relative to the static disc through the eccentric driving mechanism, so that the actions of air suction, compression and air exhaust are completed, and the operation is circulated. The following focuses on the operation and working of the moving plate 11 relative to the static plate 10:

since the second semicircular plate is located on the right side thereof with respect to the first semicircular plate as shown in fig. 3, the direction in which the movable plate 11 revolves is clockwise as shown by the circular arrow in fig. 3 to 7. If the end of the first semicircular plate is located at the right side with respect to the second semicircular plate and the radius of the left side of the circular plate a is smaller than or equal to the radius of the right side, the movable plate 11 can revolve counterclockwise. Further, since the translation direction of the solution is always towards one end of the second inner semicircular wall a2, and the second inner semicircular wall a2 is on the right side in the present schematic diagram, the simulation principle of the solution is that the translation direction is clockwise; it is clear that if the second inner semicircular wall a2 is on the left, the direction of translation is naturally counter-clockwise. The specific operation process is as follows:

taking fig. 3 as an initial position, at this time, the left end of the first inner semicircular wall a1 in the circular plate a is tangent to the left end of the inner semicircular arc wall b1 in the semicircular plate b, the tangent position is the position indicated by a straight arrow, hereinafter referred to as a left tangent point, meanwhile, the right end of the second inner semicircular wall a2 in the circular plate a is tangent to the right end of the second end semicircular arc wall b2 of the semicircular plate b, hereinafter referred to as a right tangent point, the first inner semicircular wall a1, the second inner semicircular wall a2, the inner semicircular arc wall bl, and the second end semicircular arc wall b2 form a closed space volume with the cover plate and the back plate at the two ends in the axial direction of the arc, which is called as an air cavity, and at this time, the air pressure of the air cavity ab is an initial pressure, and is in an initial state of compressed air, and the revolution angle of the movable disk 11 is set to be 0 °;

in the process that the back plate center o2 starts to revolve clockwise around the cover plate center o1 at the position shown in fig. 3 by 90 degrees until the motion track of the counter-tangential circular plate a relative to the semicircular arc plate b is shown in fig. 15, the second inner semicircular wall a2 is always tangent to the inner semicircular arc wall b1, the second end semicircular arc wall b2 is always tangent to the second inner semicircular wall a2, the space of the air cavity ab is reduced, and the air is compressed and pressurized. Namely, the left tangent point reaches the middle part of the inner semicircular arc wall b1, the right tangent point also reaches the middle part of the second inner semicircular wall a2, and the volume in the cylinder is reduced and the pressure is increased;

in the process that the back plate center o2 revolves clockwise around the cover plate center o1 at the position shown in fig. 4 for 90 degrees continuously until the position is shown in fig. 5, the motion track of the undercut circular plate a relative to the semicircular arc plate b is shown in fig. 16, the second inner semicircular wall a2 is tangent to the inner semicircular arc wall b1 all the time, the second end semicircular arc wall b2 is tangent to the second inner semicircular wall a2 all the time, the space of the air cavity ab is further reduced, and the air is compressed to the set pressure and discharged out of the air cavity ab. That is, in the position shown in fig. 4, the circular plate a with the reverse tangent continues to revolve for 90 degrees, the left tangent point and the right tangent point meet and coincide with each other at the right end point of the inner semicircular arc wall b1, at this time, the volume of the enclosed space is minimum and almost zero, the pressure of the compressed gas reaches the high pressure extreme value, and the compressed gas is discharged from the exhaust hole 107 provided in the cover plate or the semicircular arc plate b;

in the process that the back plate center o2 revolves clockwise around the cover plate center o1 at the position of fig. 5 to the position of fig. 6, the motion locus of the undercut circular plate a relative to the semicircular arc plate b is as shown in fig. 17, the second inner semicircular wall a2 is separated from the inner semicircular wall b1, the second end semicircular arc wall b2 is separated from the second inner semicircular wall a2, and the air cavity ab is in the process of revolving. That is, at the position shown in fig. 5, the circular plate a continues to revolve clockwise, and no longer contacts the semicircular plate b, and the process of revolving and idling is performed, and the contact point indicated by the arrow is in a non-contact state.

In the process that the back plate center o2 revolves clockwise around the cover plate center o1 at the position of fig. 6 to the position of fig. 7, the motion locus of the undercut circular plate a relative to the semicircular arc plate b is as shown in fig. 18, the second inner semicircular wall a2 and the inner semicircular wall b1 are tangent again from the separation, the second end semicircular arc wall b2 and the second inner semicircular wall a2 are tangent again from the separation, and the air cavity ab inhales and compresses to reenter the next compression link. That is, fig. 7, the revolution is continued by 90 degrees from the position of fig. 6, the state of the circular plate a cut reversely is returned to the state of fig. 1, the left and right cut points are reset simultaneously, and the air chamber ab is reset to the closed space volume to enter the next compression process.

As can be seen from the figure, when the volume of the air cavity ab changes, the space outside the enclosed space also changes, equivalently understood as: when the volume of the dynamic and static arc closed space is compressed and exhausted, the relatively open space simultaneously inhales gas, namely the gas cylinder inhales gas and the compression process are synchronous.

Air conditioner compressor with two assembled cylinders

The air conditioner compressor with double cylinders is different from the air conditioner compressor with single cylinder in that the structure of the cylinder 1 is different, and the other structures are the same, so the distinguishing features of the two in the aspect of the cylinder 1 are mainly described.

The specific scheme is as shown in fig. 9a, two semicircular arc plates b are arranged on the cover plate, and the two semicircular arc plates b are centrosymmetric with respect to a cover plate center o 1. The back plate is provided with two circular reverse-cutting plates a which are centrosymmetric about a back plate center o 2. And a reverse cutting circular plate a and a semi-circular arc plate b on the same side form a cylinder arc structure. It can be understood that: the undercut circular plate a and the semi-circular arc plate b of the other cylinder circular arc structure are respectively formed by rotating 180 degrees circumferentially on a circle, so that two cylinder circular arc structures with completely equal size structures are formed, however, as shown in fig. 10 to 14, at the same time point, the fit relationship between the undercut circular plate a and the semi-circular arc plate b of the two cylinder circular arc structures is always different, for example, as shown in fig. 10, the cylinder circular arc structure at the upper part in the figure is at the start time of compression, and at this time, the cylinder circular arc structure at the lower part in the figure is at the end of compression and the exhaust time.

Fig. 8 to 14 are structural and operational schematic diagrams of the double cylinder arrangement of the present invention. Wherein figure 9a is an enlarged view of figure 9 to more clearly illustrate the structural features of the dual cylinder arrangement. As shown in fig. 9a, the distance between the midpoints of the two first inner semicircular walls a1 is a semicircular midpoint connecting line H1, the distance between the midpoints of the two inner semicircular arc walls b1 is a semicircular arc midpoint connecting line H2, and the semicircular midpoint connecting line H1 is parallel to the semicircular arc midpoint connecting line H2. The connecting line of the two end points of the semicircular arc plate b is the width L1, and the connecting line of the semicircular midpoints H1 and the connecting line of the semicircular arc midpoints H2 are perpendicular to the connecting line of the two end points L1 of the semicircular arc plate b. The size relationship determines the translation engagement relationship of the movable and static disc semi-circular arc plates.

As shown in fig. 9a, the semi-circular arc midpoint connecting line H2 is equal to the sum of the diameters of the semi-circular midpoint connecting line H1 and the second inner semi-circular wall a2, and then the thickness of the semi-circular arc plate b is subtracted, that is, the semi-circular arc midpoint connecting line H2 is equal to the sum of H1 and twice the eccentricity. The semicircular midpoint connecting line H1 is equal to or greater than the sum of the diameters of the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a 3. Namely: h1 is not less than phi_a1+Φ_a2+Φ_a3。

As can be seen from fig. 10 to 14, the two inverse-cut circular plates a and the two semicircular arc plates b constitute a two-cylinder arc structure, and thus, this scheme is referred to as a two-cylinder air conditioner compressor. The cylinder arc structure is also called a cylinder unit. The two circular reverse cutting plates a integrally move together as a movable plate 11, for example, when one cylinder unit at the upper part in the figure starts compression, finishes compression and exhaust and synchronously finishes the air suction process from the figure 10 to the figure 12, the cylinder unit at the lower part starts to rotate and finishes the rotation process; when the lower cylinder unit starts to perform compression starting, compression and exhaust ending and synchronously ends the air suction process, the upper cylinder unit enters and completes the rotation process, and the process is repeated. Therefore, the cylinders of the double-cylinder scheme continuously do work within the revolution range of 360 degrees, and continuously perform the processes of air suction, compression and exhaust, thereby greatly improving the working energy density of the compressor and reducing the volume of equipment.

The specific processing structure of the dual-cylinder air-conditioning compressor is further described with reference to fig. 29 to 46 as follows:

in practice, the compressor cylinder of the invention is preferably a double-cylinder scheme in consideration of power density, convenience of processing and manufacturing and cost factors, so that the air conditioner compressor with a single cylinder is not discussed too much. The embodiments of the cylinder are further described below based on the dual cylinder solution of the present invention.

The cylinder 1 of the double-cylinder semi-arc air conditioner compressor of the invention is composed of a static disc 10 and a dynamic disc 11 as shown in figure 20. As shown in fig. 23, the stationary disc 10 has a circular cover plate 101, and two semicircular arc plates b are provided on the same side surface of the cover plate 101, one of which is referred to as a first stationary disc semicircular arc 102, and the other semicircular arc plate b is referred to as a second stationary disc semicircular arc 103. The first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 are uniformly distributed on the concentric circle of the cover plate 101, and one axial end of the first static disc semi-circular arc and one axial end of the second static disc semi-circular arc are fixedly connected with the same side face of the cover plate 101. As shown in fig. 21, the first stationary disk semi-circular arc 102 and the second stationary disk semi-circular arc 103 have the same axial height. A first inner semicircle 102b1 of the first stationary disk semicircle 102 and a second inner semicircle 103b1 of the second stationary disk semicircle 103 correspond to the inner semicircle wall b 1; the end semicircular arcs 102b2, 102b3, 103b2 and 103b3 of the first stationary disk semicircular arc 102 and the second stationary disk semicircular arc 103 correspond to the second end semicircular arc wall b2 and the first end semicircular arc wall b 3. As shown in fig. 23, the outer semicircular arc wall 102b4 of the first stationary disc semi-arc and the outer semicircular arc wall 103b4 of the second stationary disc semi-arc are both non-matching surface arcs of the cylinder structure, and have been hidden in the reinforcing and fixed supporting body of the first stationary disc semi-arc 102 and the second stationary disc semi-arc 103, there is only theoretical value in the design stage. As shown in fig. 61, the cover plate 101 may be provided at a central portion thereof with a shaft hole 104, which is a through hole for the spindle 3 to pass through. The diameter of the shaft bore 104 is greater than the maximum diameter of the shaft through which the spindle passes, whether or not it needs to pass. As shown in fig. 25, the movable plate 11 has a circular back plate 111. Two circular plates a are circumferentially and uniformly distributed by taking the circle center of one side surface of the back plate 111 as the center. The two circular reverse-cut plates a are referred to as a first circular reverse-cut plate 112 and a second circular reverse-cut plate 113, respectively, and the first circular reverse-cut plate 112 and the second circular reverse-cut plate 113 are centrosymmetric with respect to the back-plate center o 2. One axial ends of the first and second circular reverse-

cut plates

112 and 113 are fixedly connected to the same side surface of the back plate 111. The first circular reverse cutting plate 112 and the second circular reverse cutting plate 113 are physically connected, that is, connected into a whole as shown in fig. 25, and the whole has the same axial height, in other words, the first circular reverse cutting plate 112 and the second circular reverse cutting plate 113 are directly connected into a whole towards the surface of the center of the back plate 111, which is not matched with the static disc 10. As shown in fig. 25, the first outer semicircle a5 of the circular plate a with reversed cut, which is labeled 112a5 and 113a5 and the partial second outer semicircle a6, which is labeled 112a6 and 113a6 and the semicircle with non-matching end, are hidden in the whole body where the two circular plates a with reversed cut are connected, and are only the theoretical basis for design. The circular arc mating surface semi-circular arcs 112a1 and 113a1 of the movable disk 11 correspond to the first inner semi-circular wall a1 of the single cylinder solution, and the other mating surface semi-circular arcs 112a2 and 113a2 correspond to the second inner semi-circular wall a2 of the single cylinder solution. The circular arc radial end semi-circular arcs 112a3 and 113a3 of the movable disk 11, corresponding to the third end semi-circular wall a3 of the cylinder solution; the end surface of the reverse cut circular plate a not connected to the axial direction of the back plate 111 is called the circular arc end plane of the movable plate 11, and the end plane is flush. The center of the back plate 111 is provided with a shaft hole 114 with axial depth. Meanwhile, in order to reduce the weight of the movable disc 11, lightening holes 116 are uniformly distributed on a circle which takes the center of the back plate 111 as the center of a circle. As shown in fig. 26, the axial end surface of the cover plate 111, which is free from the first and second circular reverse-

cut plates

112 and 113, is provided with a key groove 117 for fitting a oldham ring of the moving disc rotation preventing device.

As shown in fig. 26, the back plate 111 is provided with a key groove 117. As shown in fig. 43, a chute 41 is provided on a base plate 43 of the cylinder chamber 4. The sliding groove 41 is positioned below the key groove 117, and the two spaces are vertical. As shown in fig. 20, the cross slip ring 8 is mounted on the lower portion of the back plate 111. As shown in fig. 42, the oldham ring 8 is composed of a ring main body 81, an upper slide key 82, and a lower slide key 83. The slip ring main body 81 is provided with an upper slide key 82 and a lower slide key 83, and the upper slide key 82 and the lower slide key 83 are spaced at 90 degrees. In order to ensure balanced stress and stable operation, two upper sliding keys 82 and two lower sliding keys 83 can be arranged on the sliding ring main body 81, the two upper sliding keys 82 are separated by 180 degrees, the two lower sliding keys 83 are separated by 180 degrees, and the upper sliding keys 82 and the lower sliding keys 83 are separated by 90 degrees. As shown in fig. 20, the sliding key 82 of the oldham ring 8 is slidably engaged with the key groove 117. The slide key 83 of the cross slide ring 8 is in sliding fit with the slide groove 41. The cross slip ring 8, the sliding groove 41 and the key groove 117 are matched to form a device for preventing the rotating disc from rotating. The cross slip ring 8 main body is not limited to a circular shape, and may be an elliptical shape or an elliptical-like shape. The output shaft of the motor 9 is butt-jointed with the spindle 3. The spindle 3 is provided with a spindle eccentric circle 32. To reduce friction, the main shaft eccentric 32 may be in supporting engagement with the main bearing 33 in the bearing housing 114.

The non-matching surfaces or outer side surfaces of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 of the embodiment of the compressor can be connected or extended to strengthen and fix the machine body, and the appearance of the machine body is cut and processed under the condition of meeting the requirement of strength design, and the parts of the machine body are straight plates and are not necessarily made into circular arc shapes.

When the compressor runs, the motor 9 drives the main shaft 3 to rotate, the main shaft 3 drives the inner ring of the main bearing 33 to rotate through the main shaft eccentric circle 32, and the outer ring of the main bearing 33 is fixedly connected with the movable disc 11 of the cylinder 1, so that the movable disc 11 is subjected to circumferential sliding and rotating pushing force from the main shaft eccentric circle 32, and the sliding and rotating radius of the movable disc is the distance between the axis of the main shaft and the circle center of the main shaft eccentric circle 32, namely the eccentric distance or the revolution radius; because the lower part of the back plate 111 is provided with the cross slip ring anti-rotation mechanism in a matching way, the movable disc 11 only does revolution motion around the main shaft 3 and can not rotate, thus ensuring that a cylinder formed by matching surfaces of the circular arcs of the movable disc and the circular arcs of the static disc is closed, compressed, exhausted, synchronously sucked and rotated, and continuously operates. The first circular plate 112 and the first semicircular arc 102 form a circular cylinder structure in a matched manner, the second circular plate 113 and the second semicircular arc 103 form another circular cylinder structure in a matched manner, and the working principle of the compression, exhaust, synchronous suction and rotation processes of the two circular cylinder structures is the same as that shown in fig. 10 to 14.

Semi-arc air conditioner compressor with three-layer and double-layer cylinders

The double-layer double-cylinder semi-arc air-conditioning compressor is characterized in that a single-layer cylinder is changed into a double-layer cylinder in the axial direction, or a layer of cylinder chamber and a cylinder with the same structural characteristics are additionally arranged at the upper end of a shell of the single-layer double-cylinder semi-arc air-conditioning compressor. Specifically, as shown in fig. 90, the cylinder chamber 4 may be provided with two layers, each layer of cylinder chamber is provided with one cylinder 1, the upper layer of cylinder chamber wall 40 is provided with at least one air inlet 42 in the radial direction, and the base plate 43 is provided with at least one air inlet 42 in the axial direction. Two air outlet holes 108 are formed in the wall 40 of each layer of the cylinder chamber, and an exhaust hole 107 is formed in the side wall of each of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 in the radial direction. The two air outlet holes 108 on the same layer are respectively communicated with the air outlet holes 107 of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 on the same layer, so as to be communicated with the inner cavity of the first static disc semi-circular arc 102 and the inner cavity of the second static disc semi-circular arc 103. Four exhaust connecting pipes 29 are arranged on the shell 2, and the four exhaust connecting pipes 29 are communicated with four air outlet holes 108 in a one-to-one correspondence manner. The inner cavity of the first stationary disk semicircular arc 102 or the inner cavity of the second stationary disk semicircular arc 103 can be communicated with the outside through an exhaust passage formed by the exhaust hole 107, the exhaust hole 108 and the exhaust connection pipe 29. Two air inlet connecting pipes 24 are arranged on the side wall of the shell 2, and the two air inlet connecting pipes 24 are communicated with the two air inlets 42 in a one-to-one correspondence manner. The specific opening position of the air inlet 42 of the upper layer and the lower layer is shown in fig. 90, the air inlet 42 is radially opened on the cylinder chamber wall 40 of the upper layer, and the air inlet 42 is axially opened on the base plate 43. The eccentric driving mechanism can be composed of a main shaft 3 and two main shaft eccentric circles 32, and the two main shaft eccentric circles 32 are axially arranged on the main shaft 3. The two main shaft eccentric circles 32 are respectively matched with the bearing chamber 114 of one cylinder 1, and in order to enable the main shaft 3 to pass through the lower cylinder 1 and be matched with the bearing chamber 114 of the upper cylinder 1, a through hole which is large enough needs to be reserved in the middle of the movable disc 11 and the static disc 10 of the lower cylinder 1. The bottom of each cylinder 1 is respectively provided with a set of device for preventing the rotation of the movable disc, the upper chute 41 for preventing the rotation of the movable disc is arranged on the cover plate 101 of the cylinder 1 below, and the lower chute 41 for preventing the rotation of the movable disc is arranged on the chassis 43.

In order to further reduce the production difficulty, as shown in fig. 61a to 61f, each of the static discs 10 is composed of two parts, one part is provided with a first static disc semi-circular arc 102, and the other part is provided with a second static disc semi-circular arc 103.

Referring to fig. 90, and in contrast to the single-layer double-cylinder semi-arc air conditioning compressor, the double-layer double-cylinder semi-arc air conditioning compressor will be further described:

the upper surface of the cover plate 101 of the lower layer cylinder is additionally provided with a sliding chute 41 for the sliding fit of the cross slip ring 8, and the sliding chute is used for matching the revolution of the upper layer moving disc 11. Referring to fig. 65, the spindle 3 is provided with two spindle eccentric circles 32, which axially correspond to the lower and upper cylinders, respectively, and are radially symmetrical at 180 ° around the spindle axis as the center of the circle. The radial mass symmetry of the double-layer eccentric circle main shaft can basically achieve natural balance, so that a mass balance block with a larger volume is not arranged. Because of the characteristic limitation of the double-layer structure, the exhaust port is configured to be complicated in structure due to axial exhaust, so the exhaust port 107 is generally configured to exhaust radially, as shown in fig. 61b and 61e, the exhaust port 107 passes through the first stationary disk semi-circular arc 102 and abuts against the exhaust port 108 along the machine body extending towards the cylinder chamber wall 40, obviously, four exhaust ports 107 correspond to four exhaust ports 108 of the cylinder chamber wall 40, and each exhaust port 108 is correspondingly communicated with one exhaust connecting pipe 29. Of course the exhaust port 107 of the upper cylinder may also be provided at the top. One air inlet connecting pipe 24 can be arranged on the shell 2 corresponding to the cylinder chamber of each layer, and two air inlet connecting pipes 24 are provided; to facilitate assembly and disassembly of the device, the stationary disc may be bisected at a line of symmetry of the arc of two halves, as shown in fig. 61a to 61 f.

The combination of the circular arc and the cover plate of the cylinder of the invention is not limited to the above mode, the cylinder embodiment is a semi-closed type, and can also be a fully-closed type with the axial end part of the circular arc connected with the cover plate, and can also be a fully-open type with the cover plates at both ends in the axial direction of the circular arc assembled and the circular arc itself, and so on, as long as the cylinder scheme formed by the combination of the semi-circular arc plate b and the reverse cutting circular plate a and the axial end cover plate of the cylinder scheme of the invention is used, the protection scope of the right of the invention is included.

The compressor cylinder structure can be used in multi-stage series connection, namely, the outlet of the first-stage cylinder is connected with the inlet of the second-stage cylinder, the outlet of the second-stage cylinder is connected with the inlet of the third-stage cylinder, and so on until a plurality of stages, and the volume of the next-stage cylinder of the series cylinder is reduced in proportion to that of the previous-stage cylinder. The multistage structure has the advantages that the pressure difference between air inlet and air outlet of each stage of cylinder can be reduced, the pressure is increased step by step, the gap leakage between the movable disc and the static disc is reduced, and the volume efficiency is improved.

According to the embodiment of the compressor, the cylinder structure of the compressor can be a single layer or multiple layers in the axial direction; the compressor can be the eccentric circle main shaft or a crankshaft main shaft with the crankshaft tip; the motor can be arranged in a totally-enclosed shell structure in the shell, or can be arranged in a semi-enclosed structure outside the shell; the structure can be a vertical structure, a horizontal structure and the like.

Fourthly, air conditioner provided with semi-arc air conditioner compressor

As shown in fig. 91, the air conditioner includes a semi-arc air conditioner compressor 01, a condenser 02, an expansion valve or capillary tube assembly 03, and an evaporator 04. The exhaust connecting pipe 29 of the semi-circular arc air-conditioning compressor 01 is communicated with the condenser 02 through a pipeline, the condenser 02 is communicated with the expansion valve or the capillary component 03 through a pipeline, the expansion valve or the capillary component 03 is communicated with the evaporator 04 through a pipeline, and the evaporator 04 is communicated with the air inlet connecting pipe 24 of the semi-circular arc air-conditioning compressor 01 through a pipeline.

The semi-circular arc air conditioner compressor 01 absorbs high-temperature low-pressure refrigerant gas from the evaporator 04, the refrigerant gas is discharged into the condenser 02 after being compressed, the refrigerant gas is discharged into the condenser 02 for heat dissipation and condensation, the low-temperature high-pressure refrigerant liquid after being cooled and liquefied enters the expansion valve or the capillary tube component 03 for pressure reduction, and then the low-temperature low-pressure refrigerant liquid enters the evaporator 04 for heat absorption and evaporation to form high-temperature low-pressure refrigerant gas which enters the semi-circular arc air conditioner compressor 01 again for compression, and the process is repeated. The air conditioner can also be provided with components such as a four-way reversing valve, a remote control circuit, artificial intelligence and the like, so that the air conditioner has more powerful functions and can meet various requirements of different customers.

Obviously, the compressor of the invention can be used for compressing conventional gas, can also be used as a pump for conveying high-pressure liquid, and can also be used for refrigeration equipment such as refrigerators, cold storages and the like.

The compressor is technically characterized by using the semi-arc air conditioner compressor cylinder scheme and the cylinder characterized by the scheme.

The terms "upper", "lower", "left" and "right" in the present specification are to be interpreted as referring to the positions of the conventional example drawings, and are not intended to limit the absolute positions and sizes of the present invention.

The above description is only for the specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and the changes or substitutions should be covered within the scope of the present invention. Therefore, all the equivalent structures or equivalent processes that are made by using the contents of the specification and the drawings of the present invention, or are directly or indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims

1. The semi-arc air-conditioning compressor comprises a compressor main body and a motor 9, a shell 2 is arranged on the peripheries of the compressor main body and the motor 9, an air inlet connecting pipe 24 and an air outlet connecting pipe 29 are arranged on the shell 2, the compressor main body is composed of an air cylinder 1 and an air cylinder chamber 4, and the air cylinder 1 is arranged in the air cylinder chamber 4; be equipped with eccentric actuating mechanism on the output shaft of motor 9, its characterized in that: the cylinder chamber 4 is provided with a chassis 43, the cylinder chamber 4 is provided with an air inlet 42, and the air inlet 42 is communicated with the air inlet connecting pipe 24;

the cylinder 1 is formed by meshing a static disc 10 and a movable disc 11, the static disc 10 is fixedly connected with the shell 2 or the cylinder chamber 4, the static disc 10 is formed by a semi-circular arc plate b and a cover plate 101, and the movable disc 11 is formed by a reverse cutting circular plate a and a back plate 111; the static disc 10 and the movable disc 11 are occluded with the circular plate a through the semicircular arc plate b, and the semicircular arc plate b and the circular plate a can be matched with the cover plate or the back plate together to form a closed air cavity ab; a bearing chamber 114 is arranged on the movable disc 11, and the eccentric driving mechanism is matched with the bearing chamber 114; the reverse cutting circular plate a is formed by connecting one end of a first semicircular plate and one end of a second semicircular plate, the opening directions of the first semicircular plate and the second semicircular plate are opposite, the diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, and the diameter of the first semicircular plate is larger than or equal to the diameter of the second semicircular plate; the center of the back plate 11 is a back plate center o2, the axis of the back plate center o2 is a back plate axis, the axis of the output shaft of the motor 9 is called a center line, and the center line is parallel to the back plate axis; the back plate 111 and the cover plate 101 are in eccentric rotary translation, and the motion mode is as follows: the axis of the back plate revolves around the central line, the revolution radius is the distance between the axis of the back plate and the central line, a device for preventing the movable disc from rotating is arranged on the back plate 111, the opening directions of the first semicircular plate and the second semicircular plate are unchanged when the movable disc rotating device can enable the back plate 111 to drive the opposite-cutting circular plate a to move relative to the semicircular plate b, and the volume of the air cavity ab can be changed when the opposite-cutting circular plate a moves relative to the semicircular plate b; the static disc 10 is provided with an exhaust hole 107, and the inner cavity of the semi-arc plate b is communicated with the exhaust connecting pipe 29 through the exhaust hole 107.

2. A semi-circular arc air conditioner compressor as claimed in claim 1 wherein: the first semi-circular plate has three side faces which are respectively a first inner semi-circular wall a1, a fourth end semi-circular wall a4 and a first outer semi-circular wall a 5; the second semicircular plate has three sides which are respectively a second inner semicircular wall a2, a third end semicircular wall a3 and a second outer semicircular wall a 6; the first inner semicircular wall a1 is connected to and tangent to the second inner semicircular wall a2, and the first outer semicircular wall a5 is connected to and tangent to the second outer semicircular wall a 6; two ends of the third end semicircular wall a3 are respectively connected with two ends of the second inner semicircular wall a2 and the second outer semicircular wall a6, and two ends of the fourth end semicircular wall a4 are respectively connected with two ends of the first inner semicircular wall a1 and the first outer semicircular wall a 5.

3. A semi-circular arc air conditioner compressor as claimed in claim 2 wherein: the side wall of the semicircular arc plate b is provided with an inner semicircular arc wall b1, an outer semicircular arc wall b4, a second end semicircular arc wall b2 and a first end semicircular arc wall b3, the inner semicircular arc wall b1 is parallel to the outer semicircular arc wall b4, one end of the inner semicircular arc wall b1 and one end of the outer semicircular arc wall b4 are respectively connected with the second end semicircular arc wall b2, the other end of the inner semicircular arc wall b1 and the other end of the outer semicircular arc wall b4 are respectively connected with the first end semicircular arc wall b3, and the diameters of the second end semicircular arc wall b2 and the first end semicircular arc wall b3 are the thickness of the semicircular arc plate b.

4. A semi-circular arc air conditioner compressor as claimed in claim 3 wherein: the sum of the diameters of the first and second inner semi-circular walls a1 and a2 is equal to the sum of the diameters of the inner semi-circular arc wall b1 and the second end semi-circular arc wall b 2.

5. A semi-circular arc air conditioner compressor as claimed in claim 2 wherein: the radius of the second inner semicircular wall a2 minus the radius of the second end semicircular arc b2 is equal to the revolution radius of the movable plate 11 when revolving relative to the stationary plate 10.

6. A semi-circular arc air conditioner compressor as claimed in claim 3 wherein: two semicircular arc plates b are arranged on the same side face of the cover plate 101, one of the semicircular arc plates is called a first static disc semicircular arc 102, the other semicircular arc plate b is called a second static disc semicircular arc 103, the first static disc semicircular arc 102 and the second static disc semicircular arc 103 are uniformly distributed on a concentric circle of the cover plate 101, and one axial end of each semicircular arc plate b is fixedly connected with the same side face of the cover plate 101; taking the center of one side face of the back plate 111 as a circle center, two circular reverse cutting plates a are uniformly distributed in the circumferential direction, the two circular reverse cutting plates a are respectively called a first circular reverse cutting plate 112 and a second circular reverse cutting plate 113, the first circular reverse cutting plate 112 and the second circular reverse cutting plate 113 are centrosymmetric about a back plate center o2, and one axial end of the first circular reverse cutting plate 112 and one axial end of the second circular reverse cutting plate 113 are fixedly connected with the same side face of the back plate 111; the first reverse cutting circular plate 112 and the first static disc semi-circular arc 102 are matched to form a cylinder circular arc structure, and the second reverse cutting circular plate 113 and the second static disc semi-circular arc 103 form another cylinder circular arc structure; two exhaust holes 107 are formed in the static disc 10, and the two exhaust holes 107 are formed in the following modes: two exhaust holes 107 are axially formed in the cover plate 101, or one exhaust hole 107 is radially formed in each of the side walls of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103; the two exhaust holes 107 are respectively communicated with the inner cavities of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 in a one-to-one correspondence mode.

7. A semi-circular arc air condition compressor as claimed in claim 6, wherein: the distance between the midpoints of the two first inner semicircular walls a1 is a semicircular midpoint connecting line H1, the distance between the midpoints of the two inner semicircular walls b1 is a semicircular arc midpoint connecting line H2, the semicircular midpoint connecting line H1 is parallel to the semicircular arc midpoint connecting line H2, the connecting line of the two end points of the semicircular arc plate b is L1, and the semicircular midpoint connecting line H1 and the semicircular arc midpoint connecting line H2 are perpendicular to the connecting line L1 of the two end points of the semicircular arc plate b.

8. A semi-circular arc air conditioner compressor as claimed in claim 7 wherein: the semi-circular arc midpoint connection H2 is equal to the semi-circular midpoint connection H1 plus the diameter of the second inner semi-circular wall a2 minus the diameter of the second end semi-circular arc wall b 2. Namely: h2 ═ H1+ Φ_a2-Φ_b2；

The connecting line H1 between the semicircular midpoints is greater than or equal to the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a3The sum of the diameters, i.e.: h1 is not less than phi_a1+Φ_a2+Φ_a3。

9. A semi-circular arc air condition compressor as claimed in claim 6, wherein: the axial height of the first inverse cutting circular plate 112 and the second inverse cutting circular plate 113 of the movable disc 11 is equal to the axial height of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 of the static disc 10, the movable disc 11 and the static disc 10 are both in dynamic clearance fit in the axial and radial directions, and the fit clearance of the tangent points of the axial and radial circular arcs is less than 0.1 mm.

10. A semi-circular arc air conditioner compressor as claimed in claim 1 wherein: the eccentric driving mechanism is composed of a main shaft 3 and a main shaft eccentric circle 32, the main shaft 3 is provided with the main shaft eccentric circle 32, and the main shaft eccentric circle 32 is matched with the bearing chamber 114.

11. A semi-circular arc air conditioner compressor as claimed in claim 1 wherein: the eccentric driving mechanism is composed of a main shaft 3 and a crankshaft tip 34, the crankshaft tip 34 is arranged at the end part of the main shaft 3, and the crankshaft tip 34 is matched with the bearing chamber 114.

12. A semi-circular arc air conditioner compressor as claimed in claim 1 wherein: the device for preventing the movable disc from rotating automatically is formed by matching a cross slip ring 8, a sliding groove 41 and a key groove 117; the back plate 111 is provided with a key groove 117, the key groove 117 and the first reverse cutting circular plate 112 are positioned at two sides of the back plate 111, the chassis 43 is provided with a sliding groove 41, the sliding groove 41 is positioned below the key groove 117, and the two spaces are vertical; the lower part of the back plate 111 is provided with a cross slip ring 8; the cross slip ring 8 is composed of a slip ring main body 81, an upper sliding key 82 and a lower sliding key 83, the slip ring main body 81 is provided with the upper sliding key 82 and the lower sliding key 83, the upper sliding key 82 and the lower sliding key 83 are separated by 90 degrees, and the upper sliding key 82 is in sliding fit with the key groove 117; the slide key 83 of the cross slide ring 8 is in sliding fit with the slide groove 41.

13. A semi-circular arc air conditioner compressor as claimed in claim 1 wherein: the cover plate 101 and the cylinder chamber 4 are matched to form a closed cylinder body, and an exhaust hole 107 is axially formed in the cover plate 101.

14. A semi-circular arc air conditioner compressor as claimed in claim 1 wherein: the semicircular plate b is radially provided with an exhaust hole 107, the chassis 43 is axially provided with a cylindrical cylinder chamber wall 40, the cylinder chamber wall 40 is radially provided with an air outlet 108, and the inner cavity of the semicircular plate b is communicated with the exhaust connecting pipe 29 through the exhaust hole 107 and the air outlet 108.

15. A semi-circular arc air condition compressor as claimed in claim 6, wherein: two layers of cylinder chamber walls 40 are axially arranged on a base plate 43 of the cylinder chamber 4, one cylinder 1 is respectively arranged in each layer of cylinder chamber wall 40, and the two cylinders 1 are sequentially arranged along the axial direction; the bearing chambers 114 of the two movable disks 11 are through holes axially penetrating through the movable disks, and the middle part of the cover plate 101 at the lower layer is provided with a shaft hole 104; an air inlet 42 is radially arranged on the upper cylinder chamber wall 40, or an air inlet 42 is arranged on the lower cover plate 101; another air inlet 42 is axially arranged on the chassis 43; two air outlet holes 108 are radially arranged on the upper cylinder chamber wall 40, or two air outlet holes 108 are axially arranged on the upper cover plate 101; two air outlet holes 108 are radially formed in the wall 40 of the lower cylinder chamber, two air exhaust holes 107 are respectively formed in the two cylinders 1, the two air outlet holes 108 in the same layer are respectively communicated with the two air exhaust holes 107 of the corresponding cylinders 1 in a one-to-one correspondence manner, and the air exhaust connecting pipe 29 is communicated with the four air outlet holes 108; the air inlet connecting pipe 24 is communicated with the two air inlets 42 in a one-to-one correspondence manner; the eccentric driving mechanism consists of a main shaft 3 and two main shaft eccentric circles 32, wherein the main shaft 3 is provided with the two main shaft eccentric circles 32, and the two main shaft eccentric circles 32 are sequentially arranged in the axial direction; the two main shaft eccentric circles 32 are respectively matched with the bearing chamber 114 of one cylinder 1; the bottom of each cylinder 1 is respectively provided with a set of device for preventing the rotation of the movable disc, the upper chute 41 for preventing the rotation of the movable disc is arranged on the cover plate 101 of the cylinder 1 below, and the lower chute 41 for preventing the rotation of the movable disc is arranged on the chassis 43.

16. A semi-circular arc air condition compressor as claimed in claim 6, wherein: each of the static discs 10 is composed of two parts, one part is provided with a first static disc semi-circular arc 102, and the other part is provided with a second static disc semi-circular arc 103.

17. A semi-circular arc air conditioner compressor as claimed in claim 10 wherein: the number of the main shaft eccentric circles 32 is two, three, four or more, and the number thereof is the same as that of the bearing chambers 114; all the spindle eccentric circles 32 are axially arranged in sequence and are uniformly distributed in the circumferential direction of the spindle 3.

18. A semi-circular arc air conditioner compressor as set forth in claim 17 wherein: the number of the spindle eccentric circles 32 is three, the axial size of the cylinder arc structure of the middle layer is two times of the axial size of the cylinder arc structures of the upper layer and the lower layer on the two sides in the axial direction, and the mass of the movable disc of the middle layer is two times of the mass of the movable disc of the upper layer and the lower layer on the two sides in the axial direction; in the axial direction, the mass center of the main shaft eccentric circle of the upper layer and the lower layer at the two ends is symmetrical to the mass center of the middle movable disc; in the radial direction, the eccentric circle of the main shaft in the middle layer is circumferentially symmetrical with the coaxial eccentric circles on two sides in the axial direction by 180 degrees of the axis of the main shaft.

19. An air conditioner equipped with a semi-circular arc air conditioner compressor according to any one of claims 1 to 18, wherein: the air conditioner comprises a semi-arc air conditioner compressor 01, a condenser 02, an expansion valve or capillary tube assembly 03 and an evaporator 04, wherein an exhaust connecting pipe 29 of the semi-arc air conditioner compressor 01 is communicated with the condenser 02 through a pipeline, the condenser 02 is communicated with the expansion valve or capillary tube assembly 03 through a pipeline, the expansion valve or capillary tube assembly 03 is communicated with the evaporator 04 through a pipeline, and the evaporator 04 is communicated with an air inlet connecting pipe 24 of the semi-arc air conditioner compressor 01 through a pipeline.