CN113738643B

CN113738643B - Semicircular arc air conditioner compressor and air conditioner thereof

Info

Publication number: CN113738643B
Application number: CN202111095721.1A
Authority: CN
Inventors: 孔祥真
Original assignee: Sanhe Tongfei Refrigeration Co ltd
Current assignee: Sanhe Tongfei Refrigeration Co ltd
Priority date: 2021-04-06
Filing date: 2021-09-17
Publication date: 2023-09-01
Anticipated expiration: 2041-09-17
Also published as: CN113653644A; CN113775522B; CN113653644B; CN113738643A; CN113738648A; CN113775522A; CN113738648B

Abstract

The semicircular arc air conditioner compressor comprises a compressor main body and a motor, wherein a shell is arranged on the periphery 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 in the cylinder chamber, an air inlet is formed in the cylinder chamber, and the air inlet is communicated with an air inlet connecting pipe; the cylinder is composed of a static disc and a dynamic disc which are meshed, and the static disc is fixedly connected with the shell or the cylinder chamber. The revolution mating surface of the cylinder is only provided with two or two pairs of arc bodies, the axial sections of the mating surfaces of the arc bodies are standard semicircles or the combination of the standard semicircles, the back plate and the cover plate can be standard whole circles or can be standard whole circle parts, the manufacturing process is simple, the mechanical processing is very easy, and the manufacturing process is simplified and the manufacturing cost is greatly reduced compared with that of a scroll compressor.

Description

Semicircular 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 semicircular arc air conditioner compressor and an air conditioner thereof.

Background

Among the various air conditioning compressors, the scroll compressor has become a hot spot of interest with its higher efficiency and more compact volume and less vibration. However, the scroll compressor has a scroll-like scroll part, and generally has a multi-scroll structure, and thus, it is difficult to manufacture the scroll compressor, and the manufacturing cost is high. Therefore, in the case of retaining many advantages of the scroll compressor, how to provide a more preferable structure, which is easier to manufacture, improves the production efficiency, and thereby reduces the manufacturing cost, has become an important 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 semicircular air conditioner compressor, the efficiency and vibration of which are substantially equivalent to those of a scroll compressor, but the structures of a movable plate and a fixed plate of a cylinder are greatly simplified, and cylinder components such as the fixed plate and the movable plate are entirely composed of semicircular arc structures and circular arc structures, which are easy to process, and compared with the scroll compressor, the manufacturing cost can be greatly reduced, and meanwhile, the manufacturing of a large-load machine type can be realized. Similarly, an air conditioner equipped with the above-described semicircular air conditioner compressor also has the above-described advantages.

The technical scheme adopted for solving the technical problems is as follows: the semi-arc air conditioner compressor is a fully-closed air conditioner compressor and is mainly used in the field of household appliances such as household air conditioner refrigeration equipment. The semicircular arc air conditioner compressor includes a compressor body and a motor 9. The motor 9 provides a rotational driving force to the compressor body. The compressor body and the outer periphery of the motor 9 are provided with a casing 2, and the casing 2 is a fully closed casing. The shell 2 can protect the compressor main body and the motor 9, is convenient for fixing and sealing the whole structure of the compressor, can make the whole compressor more compact, and is convenient for being installed in an air conditioning system. The housing 2 is provided with an inlet connection 24 and an outlet connection 29. The compressor body is composed of a cylinder 1 and a cylinder chamber 4, and the cylinder 1 is installed in the cylinder chamber 4. An eccentric driving mechanism is arranged on the output shaft of the motor 9. There are two schemes for the cylinder chamber 4: one is that the cylinder chamber 4 has only the 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 bottom plate 43 and the cylindrical cylinder chamber wall 40, and the cover plate 101 of the cylinder 1 is fixedly connected to the upper portion of the cylinder chamber wall 40. An air inlet 42 is formed in the cylinder chamber 4, 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. To facilitate heat dissipation from the motor 9, the motor 9 is typically positioned below the cylinder chamber 4 so that the gas in the housing forms an up-down convection cycle to cool the lower motor and bearings.

As shown in fig. 20, the cylinder 1 is composed of a stationary plate 10 and a movable plate 11 engaged with each other. The stationary plate 10 may be fixedly connected with 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 reverse-cut circular plate a and a back plate 111. The stationary plate 10 and the movable plate 11 are engaged with the reverse cut circular plate a through the semicircular arc plate b. A reverse cutting circular plate a and a semicircular arc plate b are matched to form a circular arc structure of the cylinder. 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 chambers ab is determined according to the number of the air chambers ab, for example, one air chamber ab is formed by only one set of reverse cutting circular plates a and semicircular arc plates b in one air chamber 1 and is called a single air chamber, and for example, two air chambers ab are formed by two sets of reverse cutting circular plates a and semicircular arc plates b in one air chamber 1 and are called double air chambers. Normally, there are two air chambers ab in one cylinder 1, so the following three structural forms of the static disc are described by taking a double cylinder as an example: full open type quiet dish, semi-open type quiet dish and full-closed type quiet dish:

as shown in fig. 48, the static disc 10 is composed of a first static disc semicircular arc 102, a second static disc semicircular arc 103 and a cover plate 101 arranged in the radial direction, wherein the cover plate 101 is a entity extending in the radial direction of the static disc semicircular arc 102 or 103, and the cover plate 101 in the form is two mutually independent parts, is positioned outside an outer semicircular arc wall b4 of the first static disc semicircular arc 102 or the second static disc semicircular arc 103 and is connected with the semicircular arc wall b4 into a whole. The cover plate 101 has a reinforcing effect on the first stationary plate semicircular arc 102 or the second stationary plate semicircular arc 103 on the one hand, and on the other hand, the connecting piece of the first stationary plate semicircular arc 102 or the second stationary plate semicircular arc 103, the first stationary plate semicircular arc 102 or the second stationary plate semicircular arc 103 can be directly fixed on the housing 2 or the cylinder chamber 4 through the cover plate 101. The movable disk that mates with the fully open stationary disk is a fully closed movable disk as shown in fig. 53 and 55, in which a first circular counter-cut plate 112 and a second circular counter-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 reverse-cut circular plate 112, the first static disc semicircular arc 102 and the two back plates; or the second reverse cutting circular plate 113 and the second static disc semicircular arc 103 can be formed by being matched with the two back plates together.

As shown in fig. 23, the semi-open type stationary disc 10 may be formed by connecting a semicircular arc plate b and a cover plate 101 in the axial direction thereof, wherein the semicircular arc plate b has two semicircular arc plates, namely a first stationary disc semicircular arc 102 and a second stationary disc semicircular arc 103, and one cover plate 101 is commonly connected to the same side in the axial direction of the first stationary disc semicircular arc 102 and the second stationary disc semicircular arc 103. The semi-open type static disc is matched with the semi-open type dynamic disc shown in fig. 25, and two reverse cutting circular plates a are shared in the figure, namely 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 together on the same side in the axial direction to one back plate 111. In this state, the closed air cavity ab is formed by the cooperation of the first reverse-cut circular plate 112 and the first static disc semicircular arc 102, and the cover plate and the back plate; or the second reverse cutting circular plate 113 and the second static disc semicircular arc 103 can be formed by being matched with the cover plate and the back plate together.

As shown in fig. 59 to 62, the totally enclosed stationary platen has two cover plates 101, and a first stationary platen semicircular arc 102 and a second stationary platen semicircular arc 103 are fixed between the two cover plates 101. The fully-opened movable disk shown in fig. 63 and 64 is matched with the fully-closed static disk, the back plate 111 is positioned between the first reverse-cut circular plate 112 and the second reverse-cut circular plate 113, and at this time, the back plate 111 is a solid structure with the reverse-cut circular plates 112 and 113 extending towards the middle in opposite directions, so as to achieve the functions of connecting and fixing the two and increasing the strength. In this state, the closed air cavity ab is formed by the cooperation of the first reverse-cut circular plate 112, the first static disc semicircular arc 102 and the two cover plates; or the second reverse cutting circular plate 113 and the second static disc semicircular arc 103 can be formed by being matched with the two cover plates together.

The cover plate 101 is a connecting piece for fixing the semicircular arc plate b, and the strength of the semicircular arc plate b is increased, and the cover plate is usually plate-shaped, and can also be in other shapes. When the reverse cutting circular plate a works relative to the semicircular arc plate b, the semicircular arc plate b can provide supporting force. The back plate 111 is a connecting piece for fixing the reverse cutting circular plate a, and the strength of the reverse cutting circular plate a is increased, and the reverse cutting circular plate a is usually plate-shaped or can be in other shapes; as shown in fig. 60 and 63, the back plate 111 is a solid connection portion between two reverse cut circular plates a.

As shown in fig. 26, the movable plate 11 is provided with a bearing chamber 114. An eccentric drive mechanism cooperates with the bearing housing 114 to drive the motion of the movable disk relative to the stationary disk. As shown in fig. 1a, the inverted cut circular plate a is formed by connecting one end of a first semicircular plate with 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 inverted cut circular plate is formed by two semicircular arcs which are circumscribed and relatively smaller on the same diameter, the opening direction of the semicircular arc is 180 degrees, and the whole inverted cut circular plate is similar to a horizontally arranged S shape. The reverse cutting circular plate is short for double outer reverse cutting semicircular arc. The diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, specifically, the diameter of the inner wall of the opening of the first semicircular plate, namely the diameter of the first outer semicircular wall a5, is collinear with the diameter of the inner wall of the opening of the second semicircular plate, namely the diameter of the second inner semicircular 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 reverse cut circular plate a is a back plate center o2, and the axis on which the back plate center o2 is located is a 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, a perpendicular line is drawn to the center line through the center of the semicircular arc plate b, and the intersection point is called a cover plate center o1. The back plate 111 and the cover plate 101 are eccentrically rotated and translated, and the motion mode is as follows: the backboard axis revolves around the center line, the revolution radius is the distance between the backboard axis and the center line, the anti-stop disc autorotation device is arranged on the backboard 111, and the anti-stop disc autorotation device can prevent the opening direction of the first semicircular plate and the second semicircular plate from being changed in the process that the backboard 111 drives the reverse cutting circular plate a to move relative to the semicircular plate b. As shown in fig. 19b, the rotation preventing means for the movable plate is generally 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 reverse cutting circular plate a relative to the semicircular plate b; the static disk 10 is provided with an exhaust hole 107, and the inner cavity of the semicircular arc plate b is communicated with the exhaust connecting pipe 29 through the exhaust hole 107.

As shown in fig. 9a to 14, the midline is shown as the cover plate center o1, and the back plate axis is shown as the back plate center o2. The back plate 111 moves relative to the cover plate 101 in the following manner: the backplate axis revolves around the midline with a revolution radius being the distance between the backplate axis and the midline, also known as the eccentricity. In the process that the back plate 111 drives the reverse cutting 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 when the reverse cutting circular plate a moves relative to the semicircular plate b; the cover plate or the semicircular plate b is provided with an exhaust hole. Since the back plate axis revolves around the center line, the movement pattern of the back plate 111 with respect to the cover plate 101 is referred to as revolution of the back plate 111 with respect to the cover plate 101 for convenience of description.

As shown in fig. 1a, the first semicircular plate has three sides, 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 with and tangent to the second inner semicircular wall a2, and the first outer semicircular wall a5 is connected with and tangent to the second outer semicircular wall a 6; the curved surface formed by the first outer semicircular wall a5 and the second outer semicircular wall a6 is parallel to the curved surface formed by the first inner semicircular wall a1 and the second inner semicircular wall a 2; the two end points of the third end semicircular wall a3 are respectively connected with the two end points of the second inner semicircular wall a2 and the second outer semicircular wall a6, and the two ends of the fourth end semicircular wall a4 are respectively connected with the 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 and the outer semicircular arc wall b4 are parallel, 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 inner semicircular wall a1 and the second inner semicircular wall a2 is equal to the sum of the diameters of the inner semicircular wall b1 and the second end semicircular wall b 2.

The diameter of the second inner semicircular wall a2 minus the thickness of the semicircular plate b is equal to the revolution diameter of the movable plate 11 when it revolves with respect to the stationary plate 10. The thickness of the semicircular plate b is equal to the diameter of b2 or b 3. The dimensional relation can ensure that when the reverse-cutting circular plate a of the movable disc moves horizontally relative to the semicircular arc plate b of the fixed disc according to a set eccentric distance, the first semicircular wall a1 is tangential to the semicircular arc plate b, meanwhile, the second semicircular wall a2 is tangential to the second 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 periodically changes from large to small or from small to large along with the revolution motion of the movable disc, so that the volume of the cylinder space also periodically changes.

As shown in fig. 23, two semicircular arc plates b are disposed on the same side of the cover plate 101, one of which is referred to as a first fixed disc semicircular arc 102, and the other semicircular arc plate b is referred to as a second fixed disc semicircular arc 103, the first fixed disc semicircular arc 102 and the second fixed disc semicircular arc 103 are uniformly distributed on a concentric circle of the cover plate 101, and one axial end is fixedly connected with the same side of the cover plate 101, that is, the first fixed disc semicircular arc 102 and the second fixed disc semicircular arc 103 are about the center of the cover plate _o 1 point symmetry, the axial height of the first stationary platen semicircle 102 is the same as that of the second stationary platen semicircle 103. As shown in fig. 25, two circular reverse-cut plates a are circumferentially uniformly distributed around the center of one side of the back plate 111, and are respectively referred to as 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 about the back plate center _o 2 are centrally symmetrical, and one axial end of the first reverse cutting circular plate 112 and one axial end of the second reverse cutting circular plate 113 are fixedly connected with the same side face of the back plate 111; the first inverted tangential circular plate 112 cooperates with the first stationary plate semicircle 102 to form a cylinder arc structure, and the second inverted tangential circular plate 113 cooperates with the second stationary plate semicircle 103 to form another cylinder arc structure. Two exhaust holes 107 are formed in the cylinder compression cavity of the static disc 10 near the compression end point, and the two exhaust holes 107 are formed in the following way: two exhaust holes 107 are axially formed in the cover plate 101, or one exhaust hole 107 is radially formed in the side wall of the first static disc semicircular arc 102 and the side wall of the second static disc semicircular arc 103 respectively; the two exhaust holes 107 are respectively communicated with the inner cavities of the first static disc semicircular arc 102 and the second static disc semicircular arc 103 in a one-to-one correspondence manner. The cover plate 101 and the back plate 111 may each be a circular plate. The inner cavity of the first static disc semicircular arc 102 and the inner cavity of the second static disc semicircular arc 103 are respectively connected with a vent hole 107 and a vent hole The exhaust passage formed by the exhaust connection pipe 29 communicates with 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 inverted cut circular plate 112 and the midpoint of the first inner semicircular wall a1 of the second inverted cut 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 fixed disc semicircular arc 102 and the midpoint of the inner semicircular arc wall b1 of the second fixed disc semicircular arc 103 is called 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 lines of the two end points of the semicircular arc plate b are of a width L1, and the semicircular midpoint connecting line H1 and the semicircular arc midpoint connecting line H2 are perpendicular to the connecting lines L1 of the two end points of the semicircular arc plate b.

The midpoint connecting line H2 of the semicircular arc is equal to: the semicircular midpoint connection H1 plus the diameter of the second inner semicircular wall a2 minus the diameter of the second end semicircular wall b2. Namely: h2 =h1+Φa2- Φb2. The dimensional relationship is an important guarantee of ensuring that the moving disc arc and the static disc arc are theoretically tangent and not rubbed when translating according to the set eccentricity.

The semicircular midpoint connecting line H1 is larger than or equal to 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. Namely: h1 More than or equal to phia1+phia2+phia3. The dimensional relationship can ensure a smaller distance between the two reverse cutting circular plates a of the movable disc arc, and simultaneously can consider that the two reverse cutting circular plates a are structurally prevented from interfering; meanwhile, the minimum reasonable distance between the end parts of the movable disc reverse cutting circular plate a and the fixed disc semicircular arc plate b is considered,

so as to ensure that the air inlet channel is unblocked.

The axial height of the first and second circular counter-cut plates 112 and 113 of the movable disk 11 is equal to the axial height of the first and second circular semi-circular arcs 102 and 103 of the static disk 10, the axial and radial directions of the movable disk 11 and the static disk 10 are in dynamic clearance fit, and the clearance between the axial and radial circular arc tangential point fit is less than 0.1mm.

As shown in fig. 19b, the housing 2 may be constituted by 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 the components may be flange-connected to a large-sized machine. The upper end of the cylinder 21 is connected with an upper end cover 22, and the lower end is connected with a lower end cover 23. The cylinder 21 has a cylinder wall provided with an air inlet connection pipe 24, a fluid supplementing port 26, and a motor junction box 20, and the upper end cover 22 has an air outlet connection pipe 29. The lower end cover is preferably an elliptical end cover, the radial direction and the cylinder 21 are concentric circles, a fixed bracket 25 can be arranged outside the bottom of the lower end cover, and an oil pump body is arranged at the center part inside the bottom; the upper end cover 22 is preferably an elliptical end cover, and the radial direction and the cylinder 21 are concentric circles. The air inlet connecting pipe 24 and the liquid supplementing 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 connected 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. An annular cavity 115 is arranged on the periphery of the bearing chamber 114, and the bearing chamber 114 is 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 crank pin 34, wherein the crank pin 34 is provided at the end of the main shaft 3, and the crank pin 34 is engaged with the bearing chamber 114. As shown in fig. 30 to 32, in order to smooth the operation of the eccentric drive mechanism, a crankshaft pin 34 is provided with a mass balance 5. As shown in fig. 33, the mass balance block 5 has a connecting disc 53, a crank pin 52 is provided in the middle of the connecting disc 53, a mounting hole 51 is provided in the crank pin 52, an arc-shaped balance block 50 is provided on the connecting disc 53, and the balance block 50 is located at the outer periphery of the crank pin 52. When installed, the crankshaft tip 34 is positioned in the mounting hole 51, the crankshaft tip sleeve 52 is positioned in the bearing chamber 114, and the counterweight 50 is positioned in the annular cavity 115. Bearing bushes may also be mounted on the exterior of the crankshaft sleeve 52. The first and second circular counter-cut plates 112 and 113 are located at both sides of the bearing chamber 114, respectively, and the first and second circular counter-cut plates 112 and 113 are centrally symmetrical about the center of the bearing chamber 114. An anti-rotation device is arranged between the movable disk 11 and the chassis 43. The back plate 111 is provided with a key slot 117, the chassis 43 of the cylinder chamber 4 is provided with a sliding slot 41, and the sliding slot 41 is positioned below the key slot 117 and is vertical to the space. 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 slip key 82, and a lower slip key 83. The slip ring main body 81 is provided with an upper sliding key 82 and a lower sliding key 83, the upper sliding key 82 and the lower sliding key 83 are spaced by 90 degrees, and the upper sliding key 82 of the cross slip 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 groove 41; the cross slip ring 8, the sliding groove 41 and the key groove 117 cooperate to form an anti-rotation device of the stop disc.

The eccentric driving mechanism may also be a second scheme as shown in fig. 29, and 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 circle 32 mates with the bearing chamber 114 of the cylinder rotor. The spindle 3 is provided with a spindle eccentric circle 32, so that such a spindle may be referred to as an eccentric circle spindle. A main bearing 33 may be installed between the eccentric circle 32 of the main shaft and the bearing housing 114 to reduce friction therebetween. In the eccentric circle spindle solution provided with the spindle eccentric circle 32, as shown in fig. 74 to 77, in order to stabilize the operation of the spindle 3, an upper bearing chamber 109 may be provided in the middle of the cover plate 101. The bearing chamber 114 is a through hole that extends axially through the rotor disk. The upper bearing 31 is mounted on the spindle 3, and the upper bearing 31 is mounted in the upper bearing chamber 109. The top of the cover plate 101 is axially provided with a cylindrical balance block chamber 110, and the upper end of the balance block chamber 110 is provided with a balance block chamber cover 100 having a sealing function. The upper end of the spindle 3 is provided with a mass balance 5 through the bearing chamber 114 and the upper bearing chamber 109 in sequence, and the mass balance 5 is located in the balance chamber 110.

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

As shown in fig. 19b, the lower end cap 23 is seen from the inside of the housing 2 upward:

the lower end of the main shaft 3 is inserted into the center of the oil pump body to be connected with a pump wheel for cooperation operation, then upwards passes through a lower bearing 211 arranged in the middle of a lower bracket 210 in a matched mode, then upwards connects and fixes the rotor and passes through a rotor of a motor 9, then upwards passes through a cross slip ring 8 in a matched mode with a main bearing 33 arranged in the center of a cylinder chamber 4, a crankshaft pin 34 at the upper end portion of the main shaft 3 is provided with a mass balance block 5, and the shaft diameter of the balance block 5 is connected with the middle of a movable disc 11 in a matched mode through a bearing or a bearing bush. The upper part of the movable disc 11 is dynamically matched with and provided with a static disc 10, as shown in fig. 24, a cover plate 101 of the static disc 10 is provided with two axial cylinder exhaust holes 107, and the exhaust holes 107 are correspondingly provided with one-way exhaust valves 290. The gas is sucked from the air inlet connecting pipe 24 of the cylinder body 21 provided with the motor 9, then enters the cylinder 1 through the air inlet 42 on the chassis 43 of the cylinder chamber 4, then the compressed high-pressure gas is discharged into the space formed by the cover plate 101 and the end closure of the upper end cover 22 through the exhaust valve 290, namely, the buffer temporary storage in the high-pressure gas chamber, and finally is discharged through the exhaust 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 is axially spaced from the motor stator mounted on the upper portion by a reasonable distance; the motor stator is fixedly connected with the inner wall of the shell body, and the upper end of the motor stator is kept at 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 with the cover plate 101 or in a matched floating connection; the cover plate 101, the cylinder chamber 4, the cylinder body 21, the motor 9, the lower bracket 210, the oil pump impeller or the gear pump driving gear and the main shaft 3 are all concentric in the axial direction.

As shown in fig. 37 to 41, the lower end of the main shaft 3 is connected with an oil pump turbine, the upper end crankshaft pin 34 is provided with a mass balance block 5, and the mass balance block 5 is in installation fit with the crankshaft pin 34 through a central installation 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 sump to an upper lubrication part through an oil pump during rotation.

Obviously, the main technical characteristics of the invention are that the semicircular cylinder disclosed by the invention is used, and other translational structures, moving parts and lubrication modes are the same as those of the conventional vortex compressor.

A third alternative of a semi-circular arc air conditioning compressor is shown in fig. 79-90.

As shown in fig. 89 or 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 integrally formed or may be of a split structure. 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 can 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 can be directly and fixedly connected with the shell 2. The bearing chambers 114 of the two movable disks 11 are through holes penetrating through the movable disks in the axial direction, and as shown in fig. 87, the middle part of the lower cover plate 101 is provided with a shaft hole 104. Two design modes of air inlet and air outlet of the two cylinders 1 are as follows:

Mode one: as shown in fig. 87, at least one air inlet 42 is formed in the lower cover plate 101, which is located outside the shaft hole 104, and another air inlet 42 is formed in the bottom plate 43 in the axial direction. Further, an axial air inlet 42 is formed at the blank of the air cavity and the chute of the lower cover plate, so that the upper cylinder 1 is in air communication with the lower cylinder 1 through the air inlet 42 on the lower cover plate 101, at this time, the upper and lower cylinders 1 can share one air inlet connecting pipe 24 for air intake, and the housing 2 is only in communication with one air inlet connecting pipe 24 with the whole cylinder chamber, that is, only one air inlet connecting pipe 24 can be provided on the housing 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 lower cylinder chamber wall 40. Two exhaust holes 107 are axially formed in the cover plate 101 of the upper-layer cylinder 1, one exhaust hole 107 is radially formed in the side wall of the first static disc semicircular arc 102 and the side wall of the second static disc semicircular arc 103 of the lower-layer cylinder 1, and 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 mode. 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 at the lower layer are respectively communicated with the inner cavity of the upper end cover 22 through a one-way valve and a communication pipe 291, and the design can ensure that the exhaust air is uniformly discharged from an exhaust connecting pipe 29 after being buffered by the inner cavity of the upper end cover 22, so that the condenser 02 can be stably supplied with air. The two air inlets 42 are axially communicated, the air inlet connecting pipe 24 is communicated with the air inlet 42 axially formed on the chassis 43, and the design has only one air inlet connecting pipe 24, so that the air conditioner compressor is smaller in size and more compact in internal structure. 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 block chamber 110, and the upper end of the balance block chamber 110 is provided with a balance block chamber cover 100 having a sealing function. The upper end of the main shaft 3 sequentially passes through the bearing chamber 114 and the upper bearing 31 of the upper bearing chamber 109, and the end of the main shaft is provided with the mass balance block 5, and the mass balance block 5 is positioned in the balance block chamber 110.

Mode two: 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 bottom plate 43. Two air outlet holes 108 are radially formed in the cylinder chamber wall 40 of each layer, and an air outlet hole 107 is radially formed in the side wall of the first static disc semicircular arc 102 and the side wall of the second static disc semicircular arc 103 respectively. The two air outlet holes 108 on the same layer are respectively communicated with the air outlet holes 107 of the first static disc semicircular arc 102 and the second static disc semicircular arc 103 on the same layer, so that the air outlet holes are communicated with the inner cavity of the first static disc semicircular arc 102 and the inner cavity of the second static disc semicircular arc 103. Four exhaust connecting pipes 29 are arranged on the shell 2, and the four exhaust connecting pipes 29 are communicated with the four air outlet holes 108 in a one-to-one correspondence. The inner cavity of the first stationary platen semicircle 102 or the inner cavity of the second stationary platen semicircle 103 may be communicated with the air inlet of the condenser 02 through an air discharge passage constituted by the air discharge hole 107, the air discharge hole 108 and the air discharge 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 positions of the air inlets 42 of 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 of the upper layer, and the air inlet 42 can be axially opened on the chassis 43. In the above-mentioned scheme, if the cylinder chamber 4 is provided with only one layer of cylinder chamber wall 40, the air inlet 42 is radially opened on the housing 2 corresponding to the upper layer of cylinder 1, so as to supply air for the upper layer of cylinder 1. Similarly, because there is no upper-layer cylinder chamber wall 40, two exhaust holes 107 of the upper-layer cylinder can be directly communicated with two upper exhaust connection pipes 29 of the upper layer of the shell 2 in a one-to-one correspondence manner, and an inner cavity of the first static disc semicircular arc 102 or the second static disc semicircular arc 103 of the upper-layer cylinder 1 can be communicated with an air inlet of the condenser 02 through an exhaust passage formed by the exhaust holes 107 and the exhaust connection 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 liquid reservoir 05 may be installed outside the air inlet connection pipe 24, and a liquid outlet of the liquid reservoir 05 is communicated with the liquid supplementing 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 main shaft 3 is axially provided with the two main shaft eccentric circles 32. The two spindle eccentric circles 32 each cooperate with a bearing chamber 114 of one cylinder 1. In order to make the spindle 3 pass through the lower cylinder 1 and cooperate with the bearing chamber 114 of the upper cylinder 1, the middle parts of the movable disc 11 and the static disc 10 of the lower cylinder 1 need to be provided with enough through holes. The bottom of each cylinder 1 is provided with a set of anti-stop disc rotation device, a chute 41 of the upper anti-moving disc rotation device is arranged on a cover plate 101 of the lower cylinder 1, and a chute 41 of the lower anti-moving disc rotation device is arranged on a chassis 43.

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

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

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

As shown in fig. 61a to 61f, each of the stationary plates 10 is composed of two parts, one part is provided with a first stationary plate semicircular arc 102, and the other part is provided with a second stationary plate semicircular 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, for the embodiment of the multi-layer cylinder, the static disc middle-split structure is easier to install and overhaul.

Further description is as follows:

first, the main working principle of the cylinder 1 is as follows: the backboard revolves around the center of the cover plate, so that the reverse cutting circular plate is driven to move relative to the semicircular arc plate. In addition, in the moving process of the reverse cutting circular plate relative to the semicircular plate, the movement conditions of all points on the reverse cutting circular plate relative to the semicircular plate are completely the same, so that the relative movement between the reverse cutting circular plate and the semicircular plate is translational movement. In the revolution process, the reverse cutting circular plate a and the semicircular arc plate b can form a relative closed space together with the cover plates and the back plates at the two ends of the height of the reverse cutting circular plate a and the semicircular arc plate b, the relative closed space is called an air cavity, and the volume of the air cavity can be gradually changed from large to small along with the revolution. Theoretically, the volume of the entire air cavity can be compressed from the original nominal design value all the way to zero, which is close to the extreme value. The radial sealing point of the cylinder compression cavity, namely the air cavity ab, surrounded by the semicircular arc and the reverse cutting circular plate is in extremely small clearance fit without contact friction. Meanwhile, the gap between the two is extremely small and smaller than 0.1mm, so that the leakage quantity is also extremely small, namely, the volumetric efficiency is higher. Optionally, in the high-pressure machine type with higher sealing requirement, the sealing element can be arranged on the circular arc axial direction, the floating structure can be adopted on the radial direction and the axial direction, and the sealing effect is enough to meet the design requirement.

In operation of the cylinder, as shown in fig. 3 to 7, the first inner semicircular wall a1 of the reverse-cut circular plate a can be tangent to the inner semicircular wall b1 of the semicircular arc plate b in a 180-degree translational range to form a tangent point on the drawing; the second inner semicircular wall a2 may be tangent to one end semicircle of the semicircular plate b in a range of 180 ° to form another tangent point on the drawing, and as shown in fig. 15 and 16, the tangent point may be relatively moved in a moving state: when the translation direction faces the second inner semicircular wall a2, the two tangent points gradually approach, and the space volume formed by the semicircular arc plate b, the reverse tangent circular plate a and the cover plate back plates at the two ends in the height direction is reduced until the space volume approaches to zero of an extreme value. And conversely, the distance between the two tangent points is gradually increased, 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 rotor 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 increased, and air suction is synchronously carried out. Therefore, the cylinder exhaust port of the present invention is provided in the semicircular arc plate b at a position near the end of the volume compression, and may be provided radially through the semicircular arc plate b or may be provided axially through the cover plate 101 in the arc height direction.

Because the cylinder scheme can only do work within 180 degrees in the translation process of the movable disc during operation, and the radius of the rotation of 180 degrees is only used for the rotation of the movable disc without doing work, the invention can adopt a double-cylinder arrangement scheme for improving the power density.

In the double cylinder arrangement scheme, as shown in fig. 8 to 14, the inverted cut circular plates a of the two cylinder structures can be manufactured into a whole, and the two semicircular arc 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 doing work in front starts the rotation process, and the whole compressor continuously works in a circle within a 360-degree rotation range.

As shown in fig. 23, the outer semicircular arc wall 103b4 of the second semicircular arc of the second fixed disk is integrally connected with the reinforced metal structure, so that the outer arc line of the outer semicircular arc wall 103b4 of the second semicircular arc of the second fixed disk is hidden in the machine body extending from the outer circle of the circular arc of the fixed disk. 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 circular arc. As shown in fig. 9a, the maximum center distance H2 of the inner circles of the two semicircular arc plates of the static disc is equal to the maximum center distance H1 of the outer circles of the circular plates of the reverse cutting of the movable disc plus the revolution diameter of the movable disc during operation. The revolution diameter is double the eccentricity. The axial height of the two circular arc plates of the static disc is equal to that of the reverse-cutting circular plate of the movable disc, so that the static disc and the movable disc can be matched to form a sealed air cavity. One end of the height of the semi-circular arc plate of the static disc is connected with the cover plate, the other end of the semi-circular arc plate of the static disc is open, and the whole cylinder volume part of the static disc is semi-open.

The backboard is circular, and two reverse-cutting circular plates are uniformly distributed on the circle taking the center of the backboard as the center of the circle. The eccentricity is the revolution distance between the circle center of the backboard and the circle center of the cover plate. As shown in fig. 25, the non-meshed cambered surfaces of the two reverse-cutting circular plates and the semi-circular plate of the static disc are respectively connected with the metal reinforced connecting structure into a whole, namely, the first outer semi-circular a5 and the second outer semi-circular a6 are connected with the metal reinforced connecting structure into a whole, so that the non-meshed surface arcs of the reverse-cutting circular plates are hidden in the circular arc body of the dynamic disc. 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 center distance H1 of the circular arcs of the two reverse cutting circular plates facing the inner circle of the semicircular plate of the static disc is larger than or equal to 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 which form the reverse cutting circular plate a, namely the center distance H1 is larger than or equal to phi _a1 +Φ _a2 +Φ _a3 It is obvious 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 . 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 open, so that the cylinder volume part of the movable plate is in a half-open form.

The axial open parts of the movable disc and the static disc are buckled together and are in axial and radial clearance fit, and as the height of the circular plate reversely cut by the movable disc is the same as that of the semicircular arc plate of the static disc, the two ends of the circular plate are closed by the cover plate and the back plate, and the arc-shaped volume formed in the radial direction is closed by two tangent points which change in the translational motion, a relatively closed air cavity ab is formed, and the space volume of the air cavity ab can be circularly changed, so that the processes of air suction, compression and air exhaust are realized in operation. The exhaust port is arranged at the end point position close to the circular arc compression of the static disc, and is radial exhaust if the exhaust port is radially arranged on the side wall of the semicircular arc plate, and is axial exhaust if the exhaust port is arranged on the cover plate. The scheme is not limited to the cross slip ring scheme, other existing mechanisms with the same function can be adopted, such as a plurality of parallel small crankshafts, one side surface of the back plate can be connected with one or more small crankshafts with the axial direction parallel to the main shaft in a matched mode, the other end of each small crankshaft is installed on the bottom plate or the static disc in a matched mode, the eccentricity of the small crankshaft and the axis of the small crankshaft is equal to that of the main shaft, the small crankshaft and the small crankshaft can form a movable disc self-transmission preventing mechanism with related bearing components and the like, and the movable disc self-transmission preventing mechanism is also arranged in a conventional mode and is not described in detail. But the cross slip ring scheme is the simplest and the lowest in processing cost. The center of the cover plate can be provided with a through main shaft through hole or not, and whether the main shaft of the translation mechanism is arranged or not mainly depends on whether the main shaft passes through the static disc or does not need to pass through the static disc, and the main shaft can be flexibly determined according to the situation by a person skilled in the art.

As shown in fig. 47 to 56, the movable disks are totally enclosed at two axial ends, i.e. two axial ends are respectively provided with a back plate with the same size, at this time, the corresponding static disk only has a semicircular arc plate and a supporting and fixing connection part thereof, and the two axial ends are not provided with cover plates. According to the scheme, the back plates are fixed at the two axial ends of the cylinder movable disc reverse-cutting circular plate, so that the strength is high, the movable disc moving quality is increased, and meanwhile, the fixed stability of the fixed disc semicircular arc plate is poor due to the fact that the axial end cover plates are not arranged.

As shown in fig. 59 and 62, the static disc of the cylinder may be fully closed at two axial ends, i.e. two axial ends are respectively connected and fixed by a cover plate with the same size, a through hole for the spindle to pass through and move is left in the middle of the cover plate, and at this time, the corresponding circular plate of the movable disc is fully opened, i.e. two axial ends of the circular plate of the movable disc are not provided with back plates, and only the circular plate of the movable disc is connected with the fixing structure and the shaft hole in the middle of the circular plate of the movable disc. The cylinder scheme has the advantages that the movable disc is light in weight and easy to process, and the movable disc reverse-cutting circular plate is reduced in strength due to the fact that the fixed supporting function of the back plate is lost, and meanwhile the autorotation preventing device of the translation mechanism of the guide actuating disc is complex to set.

The cylinder can also be of a movable disc and a static disc full-open type, namely the static disc only has an arc plate and a radial connection supporting part and has no axial two end cover plates, and the movable disc also has only a reverse cutting circular plate, a middle connection fixing part and a shaft hole and has no axial backboard. The cover plate and the back plate of the whole cylinder are independently manufactured and attached to the two axial ends of the movable disc and the static disc, and form a cylinder enclosed space volume together with the circular arc of the movable disc and the circular arc of the static disc. The scheme has the advantages that the reverse cutting circular plate and the semicircular arc plate are easier to process, the defect that the dynamic and static arc strength is reduced when the cover plate and the backboard are fixed is overcome, the stability is poor, and the rotation preventing device of the translation mechanism is particularly inconvenient to set.

The invention has the positive effects that: the operation mode and the driving mode of the air cylinder of the semicircular arc air conditioner compressor are similar to those of a vortex compressor, and are 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 air cylinder is achieved, and the purpose of compressing fluid is achieved. In theory, the movable disc and the static disc are positioned and supported in the axial radial direction, and contact friction does not occur in operation, so that the efficiency is high, meanwhile, the compression clearance of the gap between the movable disc and the static disc of the air cylinder and the volume of the air cylinder is extremely small, so that the clearance loss is small, and therefore, the device inherits various advantages of the scroll compressor. However, the air conditioner compressor of the present invention has the following advantages compared with the scroll compressor: the revolution mating surface of the cylinder is only provided with two or two pairs of arc bodies, the axial sections of the mating surfaces of the arc bodies are standard semicircles or the combination of the standard semicircles, the back plate and the cover plate can be standard whole circles or can be standard whole circle parts, the manufacturing process is simple, the mechanical processing is very easy, and the manufacturing process is simplified and the manufacturing cost is greatly reduced compared with that of a scroll compressor. Meanwhile, because 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 scheme is integrated, the equipment load can be easily increased, so that the high-efficiency high-stability large-load translational compressor can be manufactured.

Drawings

In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 to 14 are schematic structural views of a cylinder of an air conditioner compressor according to the present invention, in which the back plate 111 and the cover plate 101 are omitted for convenience of description and understanding, and the shape and the mating relationship of the core mating member reverse cut circular plate a and the semicircular plate b are protruded. Wherein fig. 1 to 7 are schematic diagrams of the single cylinder structure and the operation principle:

fig. 1 is a schematic view of a front view structure of a single cylinder, and fig. 2 is a three-dimensional schematic view of fig. 1. Fig. 3 to 7 are schematic diagrams of arc simulation operation of the movable disk 11 and the static disk 10 of the single cylinder, wherein fig. 3 is a schematic diagram of a state when the tangent point indicated by the arrow of the reverse-cut circular plate a is at zero degree, and at this time, in a compression starting state, the volume of the air cavity ab is maximum; fig. 4 to 7 are schematic views of the states of the tangential points at 90 °, 180 °, 270 ° and 360 °, respectively; fig. 1a is an enlarged schematic view of fig. 1 for describing in detail the structure of a single cylinder.

Fig. 8 to 14 are schematic structural diagrams of a two-cylinder scheme, wherein fig. 8 is a three-dimensional schematic diagram of the two-cylinder scheme. FIG. 9 is a schematic diagram of the front view of FIG. 8; FIGS. 10 to 14 are schematic diagrams of simulated operation of the two cylinder scheme; fig. 9a is an enlarged schematic view of fig. 9 for detailing structural features of the two cylinder solution.

Fig. 15 to 18 are detailed track diagrams of the change of the matching position of the reverse cutting circular plate a and the semicircular arc plate b after revolving around the semicircular arc plate b, and in fig. 15 and 16, the reverse cutting circular plate a is tangent to the semicircular arc plate b, and the actual tangent position of the reverse cutting circular plate a and the semicircular arc plate b is a line segment because the reverse cutting circular plate a and the semicircular arc plate b have certain heights. However, since this line segment is shown as only one point in the drawing, the line segment is referred to as a tangent point for descriptive convenience, and further:

FIG. 15 is a diagram showing a motion trajectory of the reverse cut circular plate a moving from a tangent point 0 to a tangent point 90 degrees relative to the semicircular plate b, the tangent point indicated by an arrow gradually moving from the leftmost end of the inner semicircular wall b1 to the center thereof along the inner semicircular wall b1, in which the first inner semicircular wall a1 is always tangent to the inner semicircular wall b1 and the second end semicircular wall b2 is always tangent to the second inner semicircular wall a 2;

FIG. 16 is a diagram showing a motion trace of the inverted tangent circular plate a moving from a tangent point 90 degrees to a tangent point 180 degrees relative to the semicircular plate b, wherein the tangent point indicated by an arrow is moved from the center of the inner semicircular wall b1 to the rightmost end thereof, and at this time, the first inner semicircular wall a1, the inner semicircular wall b1, the second end semicircular 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 wall b1 and the second end semicircular wall b2 and the second inner semicircular wall a2 are always tangent;

FIG. 17 is a diagram of a motion trajectory of 180 degrees from a tangent point to 270 degrees from a tangent point for a reverse cut circular plate a versus a semicircular plate b, with the reverse cut circular plate a gradually separated from the semicircular plate b by tangents;

fig. 18 is a diagram showing a motion trajectory of the reverse cut circular plate a moving from the tangent point 270 degrees to the tangent point 360 degrees with respect to the semicircular plate b, and the reverse cut circular plate a and the semicircular plate b gradually return to tangency from each other to start the next cycle.

Fig. 19 to 46 are schematic structural views of a first embodiment of the semicircular arc air conditioner compressor and schematic structural views of main components:

FIG. 19 is a three-dimensional schematic view of a first version of a semi-circular arc air conditioning compressor, FIG. 19a is a front view of the semi-circular arc air conditioning compressor, FIG. 19b is an enlarged schematic view of FIGS. 19aA-A in section; fig. 20 is an enlarged three-dimensional schematic view of a cylinder in a semicircular 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 static disc of FIG. 20, and FIG. 24 is a bottom view of FIG. 23; fig. 25 is a schematic view of the three-dimensional structure of the cylinder head of fig. 20, fig. 26 is a three-dimensional view of the elevation angle of fig. 25, fig. 27 is a front view of fig. 26, and fig. 28 is a cross-sectional view taken along the direction of fig. 27B-B; FIG. 29 is a perspective view of an eccentric circular spindle with main bearings, static disc bearing housing bearings, and counterweights attached thereto; fig. 30 is a three-dimensional schematic view of a crankshaft tip spindle structure of a semicircular arc air conditioner compressor with a mass balance mounted thereon, fig. 31 is a three-dimensional schematic view of fig. 30 at another angle, and fig. 32 is a front view of fig. 30; FIG. 33 is an enlarged view of the mass balance block structure of FIG. 30, FIG. 34 is an upper elevation three-dimensional view of FIG. 33, FIG. 35 is a front view of FIG. 33, and FIG. 36 is a C-C cross-sectional view of FIG. 35; FIG. 37 is a schematic view of the principal axis of the crankshaft structure of FIG. 30, FIG. 38 is a schematic view of the three-dimensional structure of FIG. 37 from another perspective, FIG. 39 is a side view of FIG. 37, FIG. 40 is a top view of FIG. 39, and FIG. 41 is a D-D sectional view of FIG. 40; fig. 42 is a schematic view of a three-dimensional structure of a cross slip ring in a semicircular 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 sectional E-E view of FIG. 44; fig. 46 is a cross-sectional view of F-F of fig. 44.

FIG. 47 is a schematic diagram of the mating structure of a fully enclosed movable disk and a fully open stationary disk; FIG. 48 is a schematic view of the G-G cross-sectional structure of FIG. 47; FIG. 49 is a schematic view of the bottom 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 fully enclosed movable disk; FIG. 53 is a schematic view of the H-H cross-sectional structure 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 diagram of the mating structure of a fully open movable disk and a fully closed stationary disk; FIG. 60 is a 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 view of a fully open movable plate; FIG. 64 is a three-dimensional view of FIG. 63;

FIG. 61a is a three-dimensional schematic view of a part of the stationary plate after being 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 about the center of the circle of the cover plate; FIG. 61b is an upper elevation three-dimensional schematic view of FIG. 61a, FIG. 61c is a front view of the static disc, FIG. 61d is a J-J cross-sectional view 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 view of the structure of the spindle, wherein two spindle eccentric circles 32 are arranged on the spindle 3;

fig. 66 to 76 are schematic structural views of a second embodiment of the semicircular arc air conditioner compressor and schematic structural views of main components:

FIG. 66 is a perspective view of a second version of the semi-circular arc air conditioning compressor; FIG. 66a is a top view of FIG. 66; FIG. 67 is an enlarged schematic view of the K-K cross-sectional structure 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 cylinder shown; FIG. 70 is a top view of FIG. 69; FIG. 71 is an L-L cross-sectional view of FIG. 70; FIG. 72 is a perspective view of FIG. 69 showing the bottom of the static disc; FIG. 73 is a bottom view of FIG. 69; FIG. 74 is a perspective view of FIG. 69, showing the top of the static disc; FIG. 75 is a perspective view of the cam shown in FIG. 68, with the bottom of the cam visible; FIG. 76 is a perspective view of the cam shown in FIG. 68, with the top of the cam visible;

fig. 77 to 90 are schematic structural views of a third embodiment of the semicircular arc air conditioner compressor and schematic structural views of main components:

FIG. 77 is a perspective view of a third aspect of the semi-circular arc air conditioner compressor; fig. 78 is a front view of fig. 77; FIG. 79 is an enlarged schematic view of the M-M cross-section of FIG. 78 showing two cylinders axially disposed; FIG. 80 is a perspective view of the double-deck cylinder of FIG. 79; FIG. 81 is another angular perspective view of the double-deck cylinder of FIG. 79; FIG. 82 is a schematic exploded view of FIG. 81, showing an upper layer having a pair of stationary and movable disks forming an upper cylinder and a lower layer having another pair of stationary and movable disks forming a lower cylinder; FIG. 83 is a front view of the static disk of the lower cylinder; FIG. 84 is a perspective view of FIG. 83, showing the bottom surface of the static disc; FIG. 85 is a top view of FIG. 83; FIG. 86 is an N-N cross-sectional view of FIG. 85; FIG. 87 is a bottom view of FIG. 83; FIG. 88 is a perspective view of FIG. 83, showing the top surface of the stationary plate provided with a keyway 117; fig. 89 is a schematic diagram of the mating structure of the upper end cap 22 and the cylinder chamber 4 with two layers of cylinder chamber walls 40, wherein the top of the upper end cap 22 is provided with an exhaust connection pipe 29, and the radial direction of the lower layer of cylinder chamber wall 40 is provided with two air outlet holes 108; fig. 90 is a schematic diagram of a matching structure of the upper end cover 22 and the cylinder chamber 4 with the double-layer cylinder chamber wall 40, wherein the side part of the upper end cover 22 is provided with an exhaust connecting pipe 29, the cylinder chamber wall 40 on the upper layer can be radially provided with an air inlet 42 and two air outlet holes 108, and the cylinder chamber wall 40 on the lower layer can be radially provided with two air outlet holes 108;

Fig. 91 is a system schematic diagram of the air conditioning structure.

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 will be apparent that the described embodiments are only some, but not all, embodiments of the invention. All other embodiments, based on the examples herein, which are within the scope of the invention as defined by the claims, will be within the scope of the invention as defined by the claims.

1. Air conditioner compressor equipped with single cylinder

As shown in fig. 1, a cylinder 1 of an air conditioner compressor includes a stationary plate 10 and a movable plate 11. The static disc 10 is composed of a semicircular arc plate b and a cover plate in the axial direction of the semicircular arc plate b, wherein the semicircular arc plate b is generally perpendicular to the cover plate. The movable plate 11 is constituted by a reverse cut circular plate a and a back plate in the axial direction of the reverse cut circular plate a, the reverse cut circular plate a being perpendicular to the back plate 111. The cover plate and the back plate are generally circular discs, and are omitted from fig. 1 to 7 in order to highlight the structural shapes of the semicircular arc plate b and the reverse-cut circular plate a. The semicircular arc plate b is matched with the reverse cutting circular plate a between the cover plate and the back plate, and the cover plate, the back plate, the semicircular arc plate b and the reverse cutting circular plate a are matched together to form a relatively closed air cavity ab. Since the air conditioner compressor of this scheme has only one air chamber ab, it is called a single cylinder air conditioner compressor.

The cylinder 1 is arranged in the cylinder chamber 4 to form a compressor main body, the motor 9 is arranged at the lower part of the compressor main body, an eccentric driving mechanism is arranged on an output shaft of the motor 9, a bearing chamber 114 is arranged on the movable disc 11, and the eccentric driving mechanism is matched with the bearing chamber 114. The motor 9 drives the movable disk 11 to eccentrically rotate and translate relative to the static disk 10 through an eccentric driving mechanism. The compressor body and the motor 9 are both mounted within the housing 2. The static plate 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 inverted 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 the diameter 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 backboard is the center of the backboard _o 2. The axis of the output shaft of the motor 9 is called the center line, the center line is parallel to the axis of the back plate, the center of the semicircular arc plate b is crossed to the center line to form a perpendicular line, and the intersection point is called the center of the cover plate _o 1. Backboard center _o The axis where 2 is located is the axis of the backboard, and the central line is parallel to the axis of the backboard. The back plate 111 moves relative to the cover plate 101 in the following manner: the backboard axis revolves around the midline, and the revolution radius is the distance between the backboard axis and the midline. In the process of driving the reverse cutting 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 all the time, namely the reverse cutting circular plate a translates or translates relative to the semicircular plate b. Translation of the reverse cutting circular plate a relative to 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 discharge, and the reverse cutting circular plate a is circulated in this way. During inspiration, gas enters the cylinder 1 sequentially through the intake nipple 24 and the intake port 42. During exhaust, high-pressure gas is sequentially discharged out of the cylinder 1 from the inner cavity of the semicircular arc plate b through the exhaust hole 107 and the exhaust connecting pipe 29.

As shown in fig. 1a, the first semicircular plate has three sides, 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 with and tangent to the second inner semicircular wall a2, the first outer semicircular wall a5 is connected with and tangent to the second outer semicircular wall a6, and the connection points on the end surfaces of the first inner semicircular wall a1 and the second inner semicircular wall a2 are also the circumscribed points of two circles where the first inner semicircular wall a1 and the second inner semicircular wall a2 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 a6. 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. The two ends of the third end semicircular wall a3 are respectively connected with the two ends of the second inner semicircular wall a2 and the second outer semicircular wall a6, and the two ends of the fourth end semicircular wall a4 are respectively connected with the two ends of the first inner semicircular wall a1 and the first outer semicircular wall a5. The third end semicircular wall a3 and the fourth end semicircular wall a4 are arranged, so that the phenomenon that the strength is weakened or the service life and the tightness are influenced due to the peak structure at the end part of the reverse cutting circular plate a can be avoided. Specifically, two ends of the inner and outer parallel equidistant arcs of the inverted tangential circular plate a are respectively provided with a third end semicircular wall a3 and a fourth end semicircular wall a4 by taking 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 semicircular end points corresponding to 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 end points corresponding to the first inner semicircular wall a1 and the first outer semicircular wall a5.

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 b3. The inner semicircular arc wall b1 and the outer semicircular arc wall b4 are formed at equal intervals, 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 thickness of the semicircular plate b can be equal to the arc thickness of the reverse-cutting circular plate a or not, and the specific situation depends on the strength design and the technical characteristics of the cylinder scheme.

As shown in fig. 1a, the sum of the diameters of the first inner semicircular wall a1 and the second inner semicircular wall a2 is equal to the sum of the diameters of the inner semicircular wall b1 and the second end semicircular 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 inverted circular plate a is referred to as the mating surface diameter of the inverted circular plate a, and the sum of the diameters of the inner semicircular wall b1 and the second end semicircular wall b2 in the semicircular plate b is referred to as the arc mating surface diameter of the semicircular 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 when the movable disk 11 revolves around the stationary disk 10. The dimensional relationship determines the fit and seal of the second end semicircular arc wall b2 end of the cylinder cavity in the revolution process of the dynamic disc and the static disc.

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

The motor 9 drives the movable plate 11 to move relative to the static plate through the eccentric driving mechanism, so that the actions of air suction, compression and air discharge are completed, and the circulation is performed. The following focuses on the action process and working mode of the movable disk 11 relative to the static disk 10:

since the second semicircular plate is located at 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 annular arrow in fig. 3 to 7. If the first semicircular plate end is located at the right side with respect to the second semicircular plate and the left radius of the reverse-cut circular plate a is smaller than or equal to the right radius, the movable plate 11 may revolve counterclockwise. Further, since the translational direction of the solution always faces one end of the second inner semicircular wall a2, the second inner semicircular wall a2 of the schematic diagram is on the right side, so that the translational direction of the schematic diagram of the solution simulation principle is clockwise; it is obvious that if the second inner semicircular wall a2 is on the left, the translational direction is naturally counterclockwise. The specific operation process is as follows:

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

in the process that the back plate center o2 starts to revolve 90 degrees clockwise around the cover plate center o1 at the position of fig. 3 to the movement track of the reverse tangent circular plate a relative to the semicircular plate b as shown in fig. 4, the second inner semicircular wall a2 is always tangent to the inner semicircular wall b1, the second end semicircular 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 boosted. That is, the left tangent point reaches the middle of the inner semicircular wall b1, and the right tangent point also reaches the middle of the second inner semicircular wall a2, at which time the volume in the cylinder becomes smaller and the pressure increases;

In the process that the back plate center o2 continuously revolves clockwise around the cover plate center o1 for 90 degrees in the position of fig. 4 until the movement track of the reverse-tangent circular plate a relative to the semicircular plate b is as shown in fig. 16, the second inner semicircular wall a2 is always tangent to the inner semicircular wall b1, the second end semicircular wall b2 is always tangent to the second inner semicircular wall a2, 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 of fig. 4, the reversely cut circular plate a continues to revolve for 90 degrees, the left cut point and the right cut point meet and coincide at the right end point of the inner semicircular arc wall b1, at this time, the volume of the closed space is minimum, 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 semicircular arc plate b;

the backplate center o2 is centered around the cover plate center in the position of FIG. 5 _o 1 continues to revolve clockwise for 90 degrees until the motion track of the reverse cutting 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 arc 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 a revolving process. That is, in the position of fig. 5, the reverse-cut circular plate a continues to revolve clockwise, is no longer tangent to the semicircular arc plate b, and enters the revolving idle process, and the tangent point state indicated by the arrow is no tangent point.

In the process that the back plate center o2 continuously revolves clockwise around the cover plate center o1 for 90 degrees in the position of fig. 6 until the motion track of the reverse cutting circular plate a relative to the semicircular plate b is as shown in fig. 18, the second inner semicircular wall a2 and the inner semicircular wall b1 are separated to be tangential again, the second end semicircular wall b2 and the second inner semicircular wall a2 are separated to be tangential again, the air cavity ab sucks and compresses, and the next compression link is reentered. In fig. 7, the revolution is continued for 90 degrees from the position of fig. 6, the state of the reverse cut circular plate a is returned to the state of fig. 1, the left and right cut points start to be simultaneously reset respectively, the air cavity ab is reformed into a closed space volume, and the next compression process is carried out.

As can be seen from the figure, when the volume of the air chamber ab changes, the space outside the enclosed space also changes, equivalently understood as: the dynamic and static circular arc enclosed space is compressed and exhausted, and simultaneously the air is sucked in the relatively open space, namely the air suction and compression processes of the air cylinder are synchronous.

2. Air conditioner compressor equipped with double cylinders

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

The specific scheme is shown in fig. 9a, two semicircular plates b are arranged on the cover plate, and the two semicircular plates b are centrally symmetrical with respect to the center o1 of the cover plate. The backboard is provided with two reverse-cutting circular plates a which are symmetrical with each other about the center o2 of the backboard. And a circular arc structure of the cylinder is formed by a reverse cutting circular plate a and a semicircular arc plate b on the same side. It can be understood that: the reverse cut circular plate a and the semicircular arc plate b of the other cylinder arc structure are respectively formed by rotating 180 degrees on a certain circle in the circumferential direction, so that two cylinder arc structures with the same size structure are formed, however, as shown in fig. 10 to 14, at the same time point, the matching relationship between the reverse cut circular plate a and one semicircular arc plate b of the two cylinder arc structures is always different, for example, as shown in fig. 10, the upper cylinder arc structure is at the starting moment of compression, and at the moment, the lower cylinder arc structure is at the ending moment of compression and the exhaust moment.

Fig. 8 to 14 are structural and operational schematic diagrams of the two-cylinder scheme according to the present invention. Wherein fig. 9a is an enlarged view of fig. 9 to more clearly illustrate the structural features of the two cylinder solution. 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 walls b1 is a semicircular midpoint connecting line H2, and the semicircular midpoint connecting line H1 and the semicircular midpoint connecting line H2 are parallel. The connecting line of two end points of the semicircular arc plate b is the width L1, and the semicircular midpoint connecting line H1 and the semicircular midpoint connecting line H2 are perpendicular to the connecting line L1 of two end points of the semicircular arc plate b. This dimensional relationship determines the translational meshing relationship of the dynamic and static disk semicircular arc plates.

As shown in fig. 9a, the semicircular midpoint connecting line H2 is equal to the sum of the diameters of the semicircular midpoint connecting line H1 and the second inner semicircular wall a2 minus the thickness of the semicircular arc plate b, i.e., the semicircular midpoint connecting line H2 is equal to the sum of H1 plus the double eccentricity. The semicircular midpoint connecting line H1 is larger than or equal to 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 Not less than phi _a1 +Φ _a2 +Φ _a3 。

As can be seen from fig. 10 to 14, the two reverse cut circular plates a and the two semicircular arc plates b constitute two cylinder circular arc structures, and thus, this scheme is called a double cylinder air conditioner compressor. The cylinder arc structure is also called a cylinder unit. The two reverse cut circular plates a move together as one movable plate 11 as a whole, for example, while the upper one of the cylinder units in the drawing starts compression, compresses, ends compression discharge and ends the suction process simultaneously from fig. 10 to 12, the lower one starts the revolution and completes the revolution process; when the lower cylinder unit starts to start compression, compresses, ends compression exhaust and synchronously ends the suction process, the upper cylinder unit enters and completes the revolution process, and the cycle is repeated. Therefore, the cylinders of the double-cylinder scheme do continuous work in the revolution range of 360 degrees, and continuously perform the air suction, compression and exhaust processes, so that the working energy density of the compressor is greatly improved, and the equipment volume is reduced.

The specific processing structure of the twin cylinder air conditioning compressor is further described below with reference to fig. 29 to 46:

because in practice, the compressor cylinder of the present invention is preferably a dual cylinder solution in view of power density and ease of manufacturing and cost considerations, a single cylinder air conditioning compressor will not be discussed in any greater detail. The following further describes embodiments of the cylinder according to the present invention based on the dual cylinder scheme.

The cylinder 1 of the double-cylinder semicircular air conditioner compressor of the invention is shown in figure 20 and consists of a static disc 10 and a movable disc 11. As shown in fig. 23, the stationary plate 10 has a circular cover plate 101, and two semicircular arc plates b are disposed on the same side of the cover plate 101, wherein one semicircular arc plate is called a first stationary plate semicircular arc 102, and the other semicircular arc plate b is called a second stationary plate 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 is fixedly connected with the same side face of the cover plate 101. As shown in fig. 21, the first stationary plate semicircular arc 102 and the second stationary plate semicircular arc 103 have the same axial height. The first inner half arc 102b1 of the first stationary plate half arc 102 and the second inner half arc 103b1 of the second stationary plate half arc 103 correspond to the inner half arc wall b1; the end half arcs 102b2, 102b3 and 103b2 and 103b3 of the first and second fixed disk half arcs 102 and 103 correspond to the second and first end half arc walls b2 and b3. As shown in fig. 23, the outer semicircular arc wall 102b4 of the first fixed disc semicircular arc and the outer semicircular arc wall 103b4 of the second fixed disc semicircular arc are non-mating surface arcs of the cylinder structure, and are hidden in the reinforcing and fixing support bodies of the first fixed disc semicircular arc 102 and the second fixed disc semicircular arc 103, so that only theoretical values in the design stage exist. 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 through which the spindle 3 passes. The diameter of the shaft bore 104 is greater than the maximum diameter of the shaft through which the spindle passes, depending on whether the spindle is required to pass therethrough. As shown in fig. 25, the movable plate 11 has a circular back plate 111. Two reverse-cutting circular plates a are uniformly distributed circumferentially around the center of one side of the back plate 111. 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, and the first circular reverse cutting plate 112 and the second circular reverse cutting plate 113 are relative to the center of the backboard _o 2 is centrosymmetric. Axial ends of the first and second circular counter-cut plates 112 and 113 are fixedly connected to the same side of the back plate 111And (5) connecting. The first reverse cutting circular plate 112 and the second reverse cutting circular plate 113 are physically connected, namely, are connected into a whole as shown in fig. 25, and the axial heights of the whole are the same, in other words, the first reverse cutting circular plate 112 and the second reverse cutting circular 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 inverted cut circular plate a is denoted as 112a5 and 113a5 and part of the second outer semicircle a6, and the non-mating end semicircle denoted as 112a6 and 113a6 are hidden in the whole connecting the two inverted cut circular plates a, which is only a theoretical basis of design. The circular arc mating surface half arcs 112a1 and 113a1 of the movable plate 11 correspond to the first inner half circular wall a1 of the single cylinder scheme, and the other mating surface half arcs 112a2 and 113a2 correspond to the second inner half circular wall a2 of the single cylinder scheme. The radial end semi-circular arcs 112a3 and 113a3 of the circular arc of the movable disc 11 are equivalent to the semi-circular wall a3 of the third end of the cylinder scheme; the axial end face of the reverse cut circular plate a, which is not connected to the back plate 111, is called the circular arc end plane of the movable plate 11, which is flush. The center of the back plate 111 is provided with an axial-depth shaft hole 114. Meanwhile, in order to reduce the weight of the movable disk 11, weight reducing holes 116 are uniformly formed on a circle centered on the center of the back plate 111. As shown in fig. 26, the cover plate 111 is provided with keyways 117 on the axial end surfaces of the first and second circular counter-cut plates 112 and 113 for mounting a cross slip ring that cooperates with the anti-rotation device of the stop disk.

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 in a chassis 43 of the cylinder chamber 4. Chute 41 is located below keyway 117 and is spatially perpendicular to both. 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 cross slip ring 8 is constituted by a slip ring main body 81, an upper slip key 82, and a lower slip 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 apart by 90 degrees. To ensure balanced stress and stable operation, two upper sliding keys 82 and two lower sliding keys 83 may be mounted on the slip ring main body 81, the two upper sliding keys 82 are spaced 180 degrees apart, the two lower sliding keys 83 are spaced 180 degrees apart, and the upper sliding keys 82 and the lower sliding keys 83 are spaced 90 degrees apart. As shown in fig. 20, the slide key 82 on the cross slide ring 8 is slidably engaged with the key groove 117. The lower sliding key 83 of the cross sliding ring 8 is in sliding fit with the sliding groove 41. The cross slip ring 8, the sliding groove 41 and the key groove 117 cooperate to form an anti-rotation device of the stop disc. The cross slip ring 8 body is not limited to a circular shape, but may be an elliptical shape or an elliptical-like shape. The output shaft of the motor 9 is butt-jointed and provided with a main shaft 3. The spindle 3 is provided with a spindle eccentric circle 32. To reduce friction, the spindle eccentric 32 may be in supporting engagement with a main bearing 33 within the bearing housing 114.

The non-mating surfaces or outer side surfaces of the first stationary platen semicircle 102 and the second stationary platen semicircle 103 in the embodiment of the compressor can be connected or extended to be a reinforced fixing machine body, and the outer shape of the machine body is cut and processed under the requirement of meeting the strength design, and the machine body is partially in a straight plate shape and does not necessarily need to be in an arc shape.

When the compressor operates, 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 air cylinder 1, so that the movable disc 11 receives a circumferential slip driving force from the main shaft eccentric circle 32, and the slip circle radius is the distance between the main shaft axis and the center of the main shaft eccentric circle 32, namely the eccentric distance or 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 disk 11 only revolves around the main shaft 3 and cannot rotate, and the cylinder formed by the circular arc of the movable disk and the circular arc matching surface of the static disk is sealed, compressed, exhausted, synchronously sucked and rotated and continuously runs. The first inverted tangential circular plate 112 and the first fixed disk semicircular arc 102 cooperate to form a cylinder circular arc structure, the second inverted tangential circular plate 113 and the second fixed disk semicircular arc 103 form another cylinder circular arc structure, and the working principles of compression, exhaust, synchronous suction and rotation processes of the two cylinder circular arc structures are the same as those shown in fig. 10 to 14.

3. Semi-circular arc air conditioner compressor with double layers and double cylinders

The double-layer double-cylinder semi-arc air conditioner compressor is characterized in that a single-layer cylinder is axially changed into a double-layer cylinder, or a layer of cylinder chamber and cylinders with the same structural characteristics are additionally arranged at the upper end of a shell of the single-layer double-cylinder semi-arc air conditioner 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, at least one air inlet 42 is radially formed on the cylinder chamber wall 40 of the upper layer, and at least one air inlet 42 is axially formed on the chassis 43. Two air outlet holes 108 are formed in the cylinder chamber wall 40 of each layer, and an air outlet hole 107 is formed in the side wall of the first static disc semicircular arc 102 and the side wall of the second static disc semicircular 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 semicircular arc 102 and the second static disc semicircular arc 103 on the same layer, so that the air outlet holes are communicated with the inner cavity of the first static disc semicircular arc 102 and the inner cavity of the second static disc semicircular arc 103. Four exhaust connecting pipes 29 are arranged on the shell 2, and the four exhaust connecting pipes 29 are communicated with the four air outlet holes 108 in a one-to-one correspondence. The inner cavity of the first stationary plate semicircle 102 or the inner cavity of the second stationary plate semicircle 103 may be communicated with the outside through an exhaust passage constituted 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 positions of the air inlets 42 of the upper layer and the lower layer are shown in fig. 90, one air inlet 42 is radially formed on the cylinder chamber wall 40 of the upper layer, and the air inlet 42 is axially formed on the chassis 43. The eccentric driving mechanism can be composed of a main shaft 3 and two main shaft eccentric circles 32, and the main shaft 3 is axially provided with the two main shaft eccentric circles 32. The two eccentric circles 32 of the main shaft are respectively matched with the bearing chambers 114 of one air cylinder 1, so that the main shaft 3 can pass through the lower air cylinder 1 to be matched with the bearing chamber 114 of the upper air cylinder 1, and the middle parts of the movable disc 11 and the static disc 10 of the lower air cylinder 1 are required to be provided with enough through holes. The bottom of each cylinder 1 is provided with a set of anti-stop disc rotation device, a chute 41 of the upper anti-moving disc rotation device is arranged on a cover plate 101 of the lower cylinder 1, and a chute 41 of the lower anti-moving disc rotation device is arranged on a chassis 43.

To further reduce the difficulty of production, as shown in fig. 61a to 61f, each of the stationary plates 10 is composed of two parts, one part is provided with a first stationary plate semicircular arc 102, and the other part is provided with a second stationary plate semicircular arc 103.

Referring to fig. 90, and in contrast to a single-layer double-cylinder half-arc air conditioning compressor, a double-layer double-cylinder half-arc air conditioning compressor is further illustrated:

the upper surface of the cover plate 101 of the lower cylinder is provided with a slide way 41 for sliding fit of the cross slip ring 8 so as to be matched with the revolution of the upper movable disk 11. Referring to fig. 65, the spindle 3 is provided with two spindle eccentric circles 32, which correspond to the lower cylinder and the upper cylinder in the axial direction, respectively, and are symmetrical at 180 ° in the radial direction with the spindle axis as the center of a circle. Because the radial mass of the double-layer eccentric circular main shaft is symmetrical, natural balance can be basically achieved, and a mass balance block with larger volume is not arranged. Because the axial exhaust of the exhaust port can result in complicated structure due to the limitation of the double-layer structure, the exhaust port 107 is generally configured to be radial exhaust, as shown in fig. 61b and 61e, the exhaust port 107 passes through the first semicircular arc 102 of the stationary disc and is attached to the butt-joint air outlet hole 108 along the direction extending towards the cylinder chamber wall 40, and obviously, four exhaust ports 107 correspond to four air outlet holes 108 of the cylinder chamber wall 40, and each air outlet hole 108 corresponds to one exhaust connection pipe 29. Of course, the exhaust hole 107 of the upper cylinder may be provided at the top. An 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 shared; to facilitate assembly and disassembly of the device, the stationary plate may be bisected into two halves at a symmetrical midline of two semicircular arcs, as shown in fig. 61a to 61 f.

The combination of the circular arc and the cover plate of the cylinder is not limited to the mode, the embodiment of the cylinder is semi-closed, the cylinder can be fully closed, the axial end parts of the circular arc are connected with the cover plate, the cover plates at the two axial ends of the circular arc are assembled, the circular arc is fully opened, and the like, so long as the cylinder scheme formed by the combination of the semi-circular arc plate b and the reverse-cutting circular plate a of the cylinder scheme and the axial end cover plates is used, and the cylinder scheme belongs to the protection scope of the invention.

The compressor cylinder structure of the invention can be used in series in multiple stages, namely, the air outlet of the first stage cylinder is connected with the air inlet of the second stage cylinder, the air outlet of the second stage cylinder is connected with the air inlet of the third stage cylinder, and the like, until a plurality of stages are reached, and the volume of the subsequent stage cylinder of the series cylinders is reduced in proportion to that of the previous stage cylinder. The multistage structure has the advantages of reducing the pressure difference between the air inlet and the air outlet of each stage of air cylinder, gradually boosting, reducing the gap leakage between the dynamic disc and the static disc and improving the volumetric efficiency.

As can be seen from the compressor embodiments, the compressor cylinder structure of the present invention may be axially single-layered or multi-layered; the compressor can be the eccentric circular main shaft or a crank shaft main shaft with the crank shaft; the motor can be a totally-enclosed shell structure in which the motor is arranged in the shell, or a semi-enclosed structure in which the motor is arranged outside the shell; the structure can be a vertical structure, a horizontal structure and the like.

4. Air conditioner equipped with semi-circular arc air conditioner compressor

As shown in fig. 91, the air conditioner includes a semicircular 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 semicircular arc air conditioner compressor 01 is communicated with the condenser 02 through a pipeline, the condenser 02 is communicated with the expansion valve or the capillary tube assembly 03 through a pipeline, the expansion valve or the capillary tube assembly 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 semicircular arc air conditioner compressor 01 through a pipeline.

The semicircular air conditioner compressor 01 absorbs high-temperature low-pressure refrigerant gas from the evaporator 04, discharges the compressed refrigerant gas into the condenser 02 for heat release and condensation, the cooled and liquefied low-temperature high-pressure refrigerant liquid enters an expansion valve or a capillary tube assembly 03 for pressure reduction, and then the low-temperature low-pressure refrigerant liquid enters the evaporator 04 for heat absorption and evaporation to be the high-temperature low-pressure refrigerant gas which enters the semicircular air conditioner compressor 01 for compression again, and the cycle is performed. The air conditioner can be further provided with four-way reversing valves, remote control circuits, artificial intelligence and other components, so that the functions of the air conditioner are more powerful, and various requirements of different customers are met.

Obviously, the compressor can compress the 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, freezers and the like.

The technical characteristics of the compressor are that the scheme of the semicircular arc air conditioner compressor cylinder and the cylinder characterized by the scheme are used.

The terms "upper", "lower", "left" and "right" in the present specification are positional interpretations made with reference to the case of the existing example drawings, and are not limiting to the absolute position and size of the present invention.

The foregoing is merely illustrative of the present invention, and the present invention is not limited thereto, and any person skilled in the art will readily recognize that variations or substitutions are within the scope of the present invention. Therefore, all equivalent structures or equivalent flow changes made by the specification and the attached drawings of the invention or directly or indirectly applied to other related technical fields are included in the protection scope of the invention.

Claims

1. A semicircular arc air conditioner compressor comprises a compressor main body and a motor (9), wherein a shell (2) is arranged on the periphery 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); an eccentric driving mechanism is arranged on an output shaft of the motor (9), and is 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 semicircular 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 meshed with the reverse cutting circular plate (a) through the semicircular arc plate (b), and 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); 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 with 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 backboard (111) is a backboard center (o 2), the axis of the backboard center (o 2) is a backboard axis, the axis of the output shaft of the motor (9) is called a midline, and the midline is parallel to the backboard 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 backboard revolves around the center line, the revolution radius is the distance between the axis of the backboard and the center line, an anti-stop disc autorotation device is arranged on the backboard (111), and the anti-stop disc autorotation device can change the volume of the air cavity (ab) when the backboard (111) drives the reverse cutting circular plate (a) to move relative to the semicircular arc plate (b) without changing the opening directions of the first semicircular plate and the second semicircular plate; an exhaust hole (107) is arranged on the static disc (10), and the inner cavity of the semicircular arc plate (b) is communicated with the exhaust connecting pipe (29) through the exhaust hole (107);

The first semicircular plate is provided with three side surfaces, namely a first inner semicircular wall (a 1), a fourth semicircular wall (a 4) and a first outer semicircular wall (a 5); the second semicircular plate is provided with three side surfaces, namely a second inner semicircular wall (a 2), a third end semicircular wall (a 3) and a second outer semicircular wall (a 6); the first inner semicircular wall (a 1) is connected with and tangent to the second inner semicircular wall (a 2), and the first outer semicircular wall (a 5) is connected with and tangent to the second outer semicircular wall (a 6); two end points of the third end semicircular wall (a 3) are respectively connected with two end points of the second inner semicircular wall (a 2) and the second outer semicircular wall (a 6), and two ends of the fourth end semicircular wall (a 4) are respectively connected with two ends of the first inner semicircular wall (a 1) and the first outer semicircular wall (a 5).

2. The semi-circular arc air conditioner compressor as set forth in claim 1, wherein: the side wall of the semicircular arc plate (b) is provided with an inner semicircular arc wall (b 1), an outer semicircular arc wall (b 4), a second end semicircular arc wall (b 2) and a first end semicircular arc wall (b 3), the inner semicircular arc wall (b 1) is parallel to the outer semicircular arc wall (b 4), one end of the inner semicircular arc wall (b 1) and one end of the outer semicircular arc wall (b 4) are respectively connected with the second end semicircular arc wall (b 2), the other end of the inner semicircular arc wall (b 1) and the other end of the outer semicircular arc wall (b 4) are respectively connected with the first end semicircular arc wall (b 3), and the diameters of the second end semicircular arc wall (b 2) and the first end semicircular arc wall (b 3) are the thickness of the semicircular arc plate (b).

3. The semi-circular arc air conditioner compressor as set forth in claim 2, wherein: the sum of the diameters of the first inner semicircular wall (a 1) and the second inner semicircular wall (a 2) is equal to the sum of the diameters of the inner semicircular arc wall (b 1) and the second end semicircular arc wall (b 2).

4. The semi-circular arc air conditioner compressor as set forth in claim 1, wherein: the radius of the second inner semicircular wall (a 2) minus the radius of the second end semicircular wall (b 2) is equal to the revolution radius of the movable disc (11) when the movable disc (11) revolves relative to the fixed disc (10).

5. The semi-circular arc air conditioner compressor as set forth in claim 2, wherein: two semicircular arc plates (b) are arranged on the same side face of the cover plate (101), one semicircular arc plate is called a first fixed disc semicircular arc (102), the other semicircular arc plate (b) is called a second fixed disc semicircular arc (103), the first fixed disc semicircular arc (102) and the second fixed disc semicircular arc (103) are uniformly distributed on a concentric circle of the cover plate (101), and one axial end of the first fixed disc semicircular arc is fixedly connected with the same side face of the cover plate (101); two reverse-cutting circular plates (a) are uniformly distributed circumferentially by taking the center of one side surface of the back plate (111) as the center of a circle, the two reverse-cutting circular plates (a) are respectively called a first reverse-cutting circular plate (112) and a second reverse-cutting circular plate (113), the first reverse-cutting circular plate (112) and the second reverse-cutting circular plate (113) are centrally symmetrical relative to the back plate center (o 2), and one axial ends of the first reverse-cutting circular plate (112) and the second reverse-cutting circular plate (113) are fixedly connected with the same side surface of the back plate (111); the first reverse cutting circular plate (112) and the first static disc semicircular arc (102) are matched to form a cylinder circular arc structure, and the second reverse cutting circular plate (113) and the second static disc semicircular 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 way: two exhaust holes (107) are axially formed in the cover plate (101), or one exhaust hole (107) is radially formed in the side wall of the first static disc semicircular arc (102) and the side wall of the second static disc semicircular arc (103) respectively; the two exhaust holes (107) are respectively communicated with the inner cavities of the first static disc semicircular arc (102) and the second static disc semicircular arc (103) in a one-to-one correspondence manner.

6. The semi-circular arc air conditioner compressor as set forth in claim 5, wherein: the distance between the midpoints of the two first inner semicircular walls (a 1) is the length of a semicircular midpoint connecting line (H1), the distance between the midpoints of the two inner semicircular walls (b 1) is the length of a semicircular midpoint connecting line (H2), the semicircular midpoint connecting line (H1) is parallel to the semicircular midpoint connecting line (H2), the two end point connecting lines of the semicircular arc plate (b) are L1, and the semicircular midpoint connecting line (H1) and the semicircular midpoint connecting line (H2) are perpendicular to the two end point connecting lines (L1) of the semicircular arc plate (b).

7. The semi-circular arc air conditioner compressor as set forth in claim 6, wherein: the length of the semicircular midpoint connecting line (H2) is equal to the length of the semicircular midpoint connecting line (H1) plus the diameter of the second inner semicircular wall (a 2) minus the diameter of the second end semicircular wall (b 2);

the length of the semicircular midpoint connecting line (H1) is larger than or equal to the sum of the diameters of the first inner semicircular wall (a 1), the second inner semicircular wall (a 2) and the third end semicircular wall (a 3).

8. The semi-circular arc air conditioner compressor as set forth in claim 5, wherein: the axial heights of the first reverse cutting circular plate (112) and the second reverse cutting circular plate (113) of the movable disc (11) are equal to the axial heights of the first static disc semicircular arc (102) and the second static disc semicircular arc (103) of the static disc (10), and the axial radial directions of the movable disc (11) and the static disc (10) are in dynamic clearance fit.

9. The semi-circular arc air conditioner compressor as set forth in claim 5, wherein: the eccentric driving mechanism consists 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).

10. The semi-circular arc air conditioner compressor as set forth in claim 1, wherein: the eccentric driving mechanism consists of a main shaft (3) and a crank shaft (34), the crank shaft (34) is arranged at the end part of the main shaft (3), and the crank shaft (34) is matched with the bearing chamber (114).

11. The semi-circular arc air conditioner compressor as set forth in claim 5, wherein: the device for preventing the rotating disc from rotating is formed by matching a cross slip ring (8), a chute (41) and a key slot (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 on 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 space of the key groove (117) and the first reverse cutting circular plate is 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), wherein the upper sliding key (82) and the lower sliding key (83) are arranged on the slip 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) 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 groove (41).

12. The semi-circular arc air conditioner compressor as set forth 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).

13. The semi-circular arc air conditioner compressor as set forth in claim 1, wherein: the semi-circular arc 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 hole (108), and the inner cavity of the semi-circular arc plate (b) is communicated with the exhaust connecting pipe (29) through the exhaust hole (107) and the air outlet hole (108).

14. The semi-circular arc air conditioner compressor as set forth in claim 5, wherein: two layers of cylinder chamber walls (40) are axially arranged on a chassis (43) of the cylinder chamber (4), one cylinder (1) is respectively arranged in each layer of cylinder chamber walls (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 which axially penetrate 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 formed on the cylinder chamber wall (40) of the upper layer, or an air inlet (42) is formed on the cover plate (101) of the lower layer; another air inlet (42) is axially formed in the chassis (43); two air outlet holes (108) are radially formed in the cylinder chamber wall (40) of the upper layer, or two air outlet holes (108) are axially formed in the cover plate (101) of the upper layer; two air outlet holes (108) are radially formed in the lower-layer cylinder chamber wall (40), two air outlet holes (107) are respectively formed in the two air cylinders (1), the two air outlet holes (108) in the same layer are respectively communicated with the two air outlet holes (107) of the corresponding air cylinders (1) in a one-to-one correspondence manner, and the air outlet connecting pipe (29) is communicated with the four air outlet holes (108); the air inlet connecting pipes (24) are 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 axially and sequentially arranged; the two main shaft eccentric circles (32) are respectively matched with bearing chambers (114) of one cylinder (1); the bottom of each cylinder (1) is provided with a set of stop disk rotation preventing device, a chute (41) of the upper stop disk rotation preventing device is arranged on a cover plate (101) of the lower Fang Qigang (1), and a chute (41) of the lower stop disk rotation preventing device is arranged on the chassis (43).

15. The semi-circular arc air conditioner compressor as set forth in claim 5, wherein: the static disc (10) is composed of two parts, wherein one part is provided with a first static disc semicircular arc (102), and the other part is provided with a second static disc semicircular arc (103).

16. The semi-circular arc air conditioner compressor as set forth in claim 9, wherein: the number of the eccentric circles (32) of the main shaft is two, three or four, and the number of the eccentric circles is the same as the number of the bearing chambers (114); all the eccentric circles (32) of the main shaft are axially arranged in sequence and are uniformly distributed in the circumferential direction of the main shaft (3).

17. The semi-circular arc air conditioner compressor as set forth in claim 16, wherein: the number of the eccentric circles (32) of the main shaft is three, the axial dimension of the circular arc structure of the air cylinder of the middle layer is equal to twice the axial dimension of the circular arc structures of the air cylinders of the upper layer and the lower layer on the two axial sides, and the moving disc mass of the middle layer is twice the moving disc of the upper layer and the lower layer on the two axial sides; the center of mass of the eccentric circles of the principal axes of the upper and lower layers at the two ends of the central movable disk is symmetrical with the center of mass of the middle movable disk in the axial direction; in the radial direction, the eccentric circle of the middle layer main shaft is circumferentially symmetrical with the coaxial eccentric circles on two sides of the axial direction by 180 degrees of the main shaft axis.

18. An air conditioner equipped with the half arc air conditioner compressor as claimed in any one of claims 1 to 17, characterized in that: the air conditioner comprises a semicircular air conditioner compressor (01), a condenser (02), an expansion valve or a capillary tube component (03) and an evaporator (04), wherein an exhaust connecting pipe (29) of the semicircular air conditioner compressor (01) is communicated with the condenser (02) through a pipeline, the condenser (02) is communicated with the expansion valve or the capillary tube component (03) through a pipeline, the expansion valve or the capillary tube component (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 semicircular air conditioner compressor (01) through a pipeline.