CN113738648B

CN113738648B - Semicircular arc compressor cylinder assembly and compressor thereof

Info

Publication number: CN113738648B
Application number: CN202111091559.6A
Authority: CN
Inventors: 孔祥真
Original assignee: Individual
Current assignee: Individual
Priority date: 2021-04-06
Filing date: 2021-09-17
Publication date: 2024-01-05
Anticipated expiration: 2041-09-17
Also published as: CN113738643B; CN113653644A; CN113738648A; CN113738643A; CN113775522A; CN113653644B

Abstract

The semicircle compressor cylinder subassembly, its characterized in that: the rotary disc comprises a static disc 10 and a movable disc 11, wherein the static disc 10 is composed of a semicircular arc plate b and a cover plate 101 in the axial direction of the semicircular arc plate b, and the movable disc 11 is composed of a reverse cutting circular plate a and a back plate 111 in the axial direction of the reverse cutting circular plate a; the semicircular arc plate b is matched with the reverse cutting circular plate a, 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 sealed air cavity (ab). The cylinder operation mode and the driving mode of the invention are similar to the scroll compressor, and are all 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 cylinder volume is extremely small, so that the volumetric efficiency is also high, and therefore, the device inherits various advantages of the scroll compressor.

Description

Semicircular arc compressor cylinder assembly and compressor thereof

Technical Field

The invention relates to the technical field of compressors, in particular to a semicircular arc compressor cylinder assembly and a compressor thereof.

Background

Among the various compressors, scroll compressors are a hot spot of interest with their higher efficiency and more compact volume and smaller 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, the present invention aims to provide a semicircular arc compressor cylinder assembly and a compressor thereof, wherein the efficiency and vibration of the semicircular arc compressor cylinder assembly are substantially equivalent to those of a scroll compressor, but the structures of a cylinder movable disc and a fixed disc are greatly simplified, and the fixed disc and the movable disc compression cylinder assembly are entirely composed of semicircular and circular structures, so that the semicircular arc compressor cylinder assembly is easy to process, and compared with the scroll compressor, the semicircular arc compressor cylinder assembly can greatly reduce the manufacturing cost and simultaneously can realize the manufacturing of a large-load machine type.

The technical scheme adopted for solving the technical problems is as follows: the semicircular arc compressor cylinder assembly comprises a fixed disc 10 and a movable disc 11. The movable disk 11 is constituted by a reverse cut circular plate a and a back plate 111 in the axial direction of the reverse cut circular plate a.

The static disc has the following three structural forms, namely a fully-opened static disc, a semi-opened static disc and a fully-closed static disc:

as shown in fig. 48, the static disc 10 may be formed by only a semicircular arc plate b, and the semicircular arc plate b may be directly fixed in a casing 1c2 of the air compressor, wherein a bottom plate 1c27 of the casing is a cover plate 101, and a center of the bottom plate 1c27 is a cover plate center o1; in the figure, the number of semicircular arc plates b is two, namely a first semicircular arc 102 of the fixed disk and a second semicircular arc 103 of the fixed disk. This is a fully open static disc. 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 semicircular arc plate b and the reverse-cutting circular plate a can cooperate with the two back plates to form a sealed air cavity (ab).

As shown in fig. 35, the semi-open type stationary disc 10 may be formed by connecting a semicircular arc plate b and a cover plate 101, 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 connected to the same side of the first stationary disc semicircular arc 102 and the second stationary disc semicircular arc 103 in the axial direction. The semi-open type static disc is matched with the semi-open type dynamic disc as shown in fig. 41, and a back plate 111 is commonly connected to the same side of the first reverse cutting circular plate 112 and the second reverse cutting circular plate 113 in the axial direction in the figure. In this state, the semicircular arc plate b and the reverse cutting circular plate a can be matched with the cover plate and the back plate together to form a sealed air cavity (ab).

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, and the back plate 111 is positioned between the first reverse cutting circular plate 112 and the second reverse cutting circular plate 113 and only plays a role of connecting and fixing the first reverse cutting circular plate 112 and the second reverse cutting circular plate. In this state, the semicircular arc plate b and the reverse-cutting circular plate a can be matched with the two cover plates together to form a sealed air cavity (ab).

The cover plate 101 is a connecting piece for fixing the semicircular arc plate b, is usually plate-shaped, can also be in other shapes, and can only provide supporting force for the semicircular arc plate b when the reverse cutting circular plate a moves relative to the semicircular arc plate b; as shown in fig. 48, the cover plate 101 is only a portion outside the outer semicircular arc wall b4 of the first and second fixed disk semicircular arcs 102 and 103, and is a connecting member for fixing the first and second fixed disk semicircular arcs 102 and 103 to the cylinder case, and in this embodiment, the first and second fixed disk semicircular arcs 102 and 103 are independent members. The back plate 111 is a connecting piece for fixing the reverse cutting circular plate a, is usually plate-shaped, can also be in other shapes, and drives the reverse cutting circular plate a to work against the semicircular plate b in the above movement mode by driving the back plate; as shown in fig. 60 and 63, the back plate 111 is a connecting portion between two reverse cut circular plates a.

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 sealed air cavity (ab). The inverted 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, specifically, the diameter of the inner wall of the opening of the first semicircular plate, namely the diameter of the first outer semicircular plate 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 center of the backboard is backboard center o2, and the center of the cover board is cover board center o1. The axis of the backboard center o2 is a backboard axis, the axis of the cover board center o1 is a cover board axis, and the cover board axis is parallel to the backboard axis. As shown in fig. 9a to 14, the cover plate axis is shown as a cover plate center o1, and the back plate axis is shown as a back plate center o2. The back plate 111 moves relative to the cover plate 101 in the following manner: the back plate axis revolves around the cover plate axis with a revolution radius that is the distance between the back plate axis and the cover plate axis, also referred to as eccentricity. 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 cover plate axis, the manner of movement of the back plate 111 relative to the cover plate 101 is referred to as revolution of the back plate 111 relative to the cover plate 101 for convenience of description.

The first semicircular plate is provided with three side surfaces, namely a first inner semicircular wall a1, a fourth semicircular wall a4 and a first outer semicircular wall a5; 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 moves from large to small or from small to large along with the revolution movement of the movable disc, so that the space volume of the cylinder also periodically changes.

The cover plate is provided with two semicircular plates b which are symmetrical with each other about 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; 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, the semicircular midpoint connecting line H1 is parallel to the semicircular midpoint connecting line H2, the connecting lines of the two end points of the semicircular plates b are the width L1, and the semicircular midpoint connecting line H1 and the semicircular midpoint connecting line H2 are perpendicular to the connecting lines L1 of the two end points of the semicircular plates b; the inverted tangential circular plate a and the semicircular arc plate b on the same side form a cylinder arc structure.

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 b 2. Namely: h2 =h1+Φ _a2 -Φ _b2 . 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 a 3. Namely: h1 Not less than phi _a1 +Φ _a2 +Φ _a3 . 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 fact that the minimum reasonable distance is kept between the end parts of the movable disc reverse-cutting circular plate a and the fixed disc semicircular arc plate b is considered, so that the smoothness of an air inlet channel is ensured.

The stationary disc 10 has a circular cover plate 101, two semicircular arc plates b are arranged on the same side surface of the cover plate 101, one of the semicircular arc plates is called a first stationary disc semicircular arc 102, the other semicircular arc plate b is called a second stationary disc semicircular arc 103, the first stationary disc semicircular arc 102 and the second stationary disc semicircular arc 103 are uniformly distributed on a concentric circle of the cover plate 101, one axial end of the first stationary disc semicircular arc 102 is fixedly connected with the same side surface of the cover plate 101, and the axial height of the first stationary disc semicircular arc 102 and the axial height of the second stationary disc semicircular arc 103 are the same; the middle part of the cover plate 101 is provided with a shaft hole 104; the movable disc 11 has a circular back plate 111, two reverse-cutting circular plates a are circumferentially and uniformly distributed around the center of a circle on one side of the back plate 111, 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 about the back plate center o2, 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 of the back plate 111; a spindle hole 114 with axial depth is arranged at the center of the back plate 111; weight reducing holes 115 are uniformly distributed on a circle taking the circle center of the main shaft hole 114 as the circle center; a key groove 116 is provided on an axial end face of the other side face of the back plate 111.

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.

The air compressor equipped with the half arc compressor cylinder assembly includes a housing 1c2, the housing 1c2 may be cylindrical, and the housing 1c2 is composed of an upper cover 1c22, a cylinder 1c21 and a bottom plate 1c 27. The lower end of the cylinder 1c21 is connected with a bottom plate 1c27 of the shell; the cylinder wall of the cylinder 1c21 is provided with an air inlet 1c24 penetrating through the cylinder wall; the upper end of the cylinder 1c21 is flanged to the upper cover 1c22 of the housing; the cylinder 1c1 is installed in the cavity of the shell 1c2, the cylinder 1c1 is formed by matching a cylinder static disc 1c10 and a cylinder dynamic disc 1c11, and the cylinder static disc 1c10 is dynamically matched with the cylinder dynamic disc 1c11 axially downwards. The cylinder static disc 1c10 is fixedly connected with the shell 1c2, specifically, the upper cover 1c22 can be clung to the lower end face of the upper cover in the axial direction to install the cylinder static disc 1c10, and the cylinder static disc 1c10 is static relative to the upper cover 1c 22.

The cylinder static disc 1c10 is provided with a static disc cover plate 1c101, the center of the static disc cover plate 1c101 is provided with a shaft hole 1c104, and one side of the static disc cover plate 1c101 is provided with a first static disc semicircular arc 1c102 and a second static disc semicircular arc 1c103. The first static disc semicircular arc 1c102 and the second static disc semicircular arc 1c103 are symmetrically distributed about the center point of the static disc cover plate 1c101, and the center is the cover plate center o1. The cylinder static disc 1c10 is provided with an exhaust channel, the exhaust channel is composed of an exhaust hole and an exhaust pipe, the exhaust pipe is arranged on the static disc cover plate 1c101 or on the side wall of the cylinder 1c21, the exhaust pipe is communicated with the outside of the shell 1c2, and the inner cavity of the first static disc semicircular arc 1c102 and the inner cavity of the second static disc semicircular arc 1c103 are respectively communicated with one exhaust channel.

The cylinder movable disk 1c11 is formed by connecting a movable disk back plate 1c111, a first cylinder movable disk arc 1c112, a second cylinder movable disk arc 1c113 and a bearing chamber 1c 114. The first cylinder disc arc 1c112 and the second cylinder disc arc 1c113 have the same shape as the reverse cut circular plate a shown in fig. 1, and are each formed by connecting a first semicircular plate and a second semicircular plate. The bearing chamber 1c114 is positioned at the central part of the movable disc back plate 1c111, the central part of the movable disc back plate 1c111 is provided with a shaft hole 1c115, and the bearing chamber 1c114 and the shaft hole 1c115 are correspondingly concentric; the first cylinder disc arc 1c112 and the second cylinder disc arc 1c113 are located on both sides of the bearing chamber 1c114, respectively, and the first cylinder disc arc 1c112 and the second cylinder disc arc 1c113 are center-symmetrical with respect to the center of the bearing chamber 1c 114. An anti-stop disk rotation device is arranged between the cylinder moving disk 1c11 and the bottom plate 1c 27. The end face of the movable disc back plate 1c111, facing the bottom plate 1c27, is provided with a key groove 1c117, the bottom plate 1c27 is provided with a sliding groove 1c271, the sliding groove 1c271 is positioned below the key groove 1c117, and the two are vertical in space; a cross slip ring 1c8 is arranged at the lower part of the movable disc backboard 1c 111; the cross slip ring 1c8 is composed of a slip ring main body 1c81, an upper sliding key 1c82 and a lower sliding key 1c83, the upper sliding key 1c82 and the lower sliding key 1c83 are arranged on the slip ring main body 1c81, the upper sliding key 1c82 and the lower sliding key 1c83 are separated by 90 degrees, and the upper sliding key 1c82 of the cross slip ring 1c8 is in sliding fit with the key groove 1c 117; the cross slip ring 1c8 is provided with a down-sliding key 1c83 which is in sliding fit with the sliding groove 1c 271; the cross slip ring 1c8, the chute 1c271 and the key groove 1c117 cooperate to constitute an anti-rotation device for the stopper disk. The device for preventing the automatic transmission of the movable disk can be a cross slip ring automatic transmission preventing device, and can also be other homofunctional devices formed by a plurality of small crankshafts with the axial direction parallel to the main shaft and the eccentric distance equal to the main shaft. The first cylinder movable disc arc 1c112 and the first static disc half arc 1c102 are matched to form a cylinder arc structure, and the second cylinder movable disc arc 1c113 and the second static disc half arc 1c103 form another cylinder arc structure.

The housing 1c2 is provided with a motor 1c9, and with reference to fig. 65-68, an eccentric drive mechanism is mounted on the output shaft of the motor 1c9. The eccentric drive mechanism is engaged with the bearing chamber 1c 114. The motor 1c9 is specifically mounted in such a manner that a motor bracket 1c26 is provided on the upper cover 1c22, and the motor 1c9 is mounted on the motor bracket 1c 26. The eccentric drive mechanism has two modes:

first, as shown in fig. 68, the eccentric drive mechanism is composed of a spindle 1c3 and a spindle eccentric circle 1c32, and the spindle eccentric circle 1c32 is provided at the lower part of the spindle 1c 3. As shown in fig. 67, the spindle eccentric circle 1c32 is fitted in the bearing chamber 1c114 of the cylinder block. The lower part of the spindle 1c3 is provided with a spindle eccentric circle 1c32, and thus may be referred to as an eccentric spindle. A main bearing 1c6 may be installed between the eccentric circle 1c32 of the main shaft and the bearing housing 1c114 to reduce friction therebetween. In actual processing, the main shaft 1c3 further includes an upper shaft diameter 1c31, a lower shaft diameter 1c33, and a weight-saving hole 1c34.

As shown in fig. 84, the eccentric drive mechanism includes a crankshaft 2c3 and a crankshaft tip 2c34, and the crankshaft tip 2c34 is provided at the lower portion of the crankshaft 2c 3. The distance between the axis of the crankshaft tip 2c34 and the axis of the crankshaft 2c3 diameter 2c31 is the eccentricity. As shown in fig. 83, the crankshaft tip 2c34 is fitted with a bearing housing. To reduce friction, a center bearing 2c6 is installed between the crankshaft tip 2c34 and the bearing housing.

And a balance block 1c4 is arranged on the main shaft 1c 3.

The two long side surfaces of the key slot 1c117 are provided with long strip-shaped bosses 1c118 which are fixedly connected with the movable disk back plate 1c111 so as to form a sliding key slot 1c117. The key groove 1c117 may be formed directly on the corresponding side of the back plate, and is directly machined by a planer or a milling machine, without the need to provide the elongated boss 1c118.

A first exhaust pipe 1c105 and a second exhaust pipe 1c106 are arranged on one side of the static disc cover plate 1c101 corresponding to the upper cover 1c22, a first exhaust hole 1c107 and a second exhaust hole 1c108 are axially formed in the static disc cover plate 1c101, the first exhaust hole 1c107 and the first exhaust pipe 1c105 are connected into an exhaust channel, and the second exhaust hole 1c108 and the second exhaust pipe 1c106 are connected into another exhaust channel; the first exhaust hole 1c107 is communicated with the inner cavities of the first exhaust pipe 1c105 and the second static disc semicircular arc 1c103, and the second exhaust hole 1c108 is communicated with the inner cavities of the second exhaust pipe 1c106 and the first static disc semicircular arc 1c 102; the upper cover 1c22 is provided with two circular holes 1c23, and the two circular holes 1c23 are respectively matched with the first exhaust pipe 1c105 and the second exhaust pipe 1c 106.

A first exhaust hole 1c107 is radially formed in the second static disc semicircular arc 1c103, a second exhaust hole 1c108 is radially formed in the first static disc semicircular arc 1c102, a first exhaust pipe 1c105 and a second exhaust pipe 1c106 are radially arranged on the side wall of the cylinder 1c21, the first exhaust hole 1c107 and the first exhaust pipe 1c105 are connected into one exhaust passage, and the second exhaust hole 1c108 and the second exhaust pipe 1c106 are connected into the other exhaust passage; the first exhaust hole 1c107 is communicated with the inner cavities of the first exhaust pipe 1c105 and the second static disc semicircular arc 1c103, and the second exhaust hole 1c108 is communicated with the inner cavities of the second exhaust pipe 1c106 and the first static disc semicircular arc 1c 102.

The shell 1c2 is provided with two cylinders 1c21 which are axially overlapped, the top of the upper cylinder 1c21 is connected with the upper cover 1c22, and the bottom of the lower cylinder 1c21 is connected with the bottom plate 1c 27; an air inlet 1c24 penetrating through the cylinder wall is formed in the cylinder wall of each cylinder 1c21, and a first exhaust pipe 1c105 and a second exhaust pipe 1c106 are radially arranged on the cylinder wall of each cylinder 1c 21; two sets of air cylinders 1c1 are axially arranged in the shell 1c2, two spindle eccentric circles 1c32 are arranged on the spindle 1c3, the two spindle eccentric circles 1c32 are axially and sequentially arranged, the two spindle eccentric circles 1c32 are radially symmetrical about the spindle axis by 180 degrees, and each of the two spindle eccentric circles 1c32 is matched with a bearing chamber 1c114 of one air cylinder 1c 1; the bottom of each cylinder 1c1 is provided with a set of anti-stop disc rotation device, a chute 1c271 of the upper anti-moving disc rotation device is arranged on a static disc cover plate 1c101 of the lower cylinder 1c1, and a chute 1c271 of the lower anti-moving disc rotation device is arranged on a bottom plate 1c 27.

The number of the spindle eccentric circles 1c32 may be two, three, four or more, and the number of the spindle eccentric circles 1c32 is the same as the number of the bearing chambers 1c 114. Alternatively, all the spindle eccentric circles 1c32 are axially arranged in order and are uniformly distributed in the circumferential direction of the spindle 1c3, for example, the spatial angle is 180 degrees when the spindle eccentric circles 1c32 are two, the spatial angle is 120 degrees when the spindle eccentric circles 1c32 are three, and so on.

As shown in fig. 95 to 100, each cylinder static disc 1c10 is composed of two parts, wherein one part is provided with a first static disc semicircular arc 1c102, and the other part is provided with a second static disc semicircular arc 1c103. The cylinder static disc 1c10 is divided into two parts to be respectively manufactured, so that the manufacturing 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:

firstly, the structure of the cylinder assembly mainly comprises a semicircular arc plate, another double outer reverse cutting semicircular arc plate and cover plates at two ends of the height of the semicircular arc plate. The double outer reverse-cut semicircular arc can be called reverse-cut circular plate for short. The reverse cutting circular plate is composed of two semicircular arcs which are circumscribed and are relatively smaller on the same diameter, and the opening direction of each semicircular arc is 180 degrees. The semicircular arc plate and the reverse cutting circular plate move relatively, wherein the static arc is a static disc arc, and the moving arc is a moving disc arc. The movable disc arc can revolve around the center of the cover plate by taking the set eccentricity as the radius under the dragging of the driving mechanism, so that the movable disc arc moves relative to the fixed disc arc, and therefore the connecting diameter of the fixed disc arc end point and the connecting diameter of the movable disc arc end point are always parallel in movement.

The main working principle of the cylinder assembly 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 moving disc arc and the static disc arc can form a relative closed space together with the cover plates and the back plates at the two ends of the height of the moving disc arc and the static disc arc, the relative closed space can be called an air cavity, the volume of the air cavity can gradually change from large to small along with the revolution, and theoretically, the volume of the whole air cavity can be always compressed to zero close to an extreme value from an initial rated design 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 assembly, 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 within a translation range of 180 degrees to form a tangent point; the second inner semicircular wall a2 may be tangent to one end semicircle of the semicircular plate b within a range of 180 ° to form another tangent point, 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 direction of translation of the rotor of the cylinder assembly 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 is arranged in the semicircular arc plate b at a position close to the volume compression end point, and can radially pass through the semicircular arc plate b or axially pass through the cover plate 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.

The double-cylinder arrangement scheme is that, as shown in fig. 8 to 14, on the basis of the single-cylinder assembly shown in fig. 1 to 7, one point is taken as the circle center of revolution on the diameter or the extension line of the diameter of the connecting line of the two end points perpendicular to the semicircular plate b, and the semicircular plate b and the inverted tangential circular plate a are rotated 180 degrees to form two cylinder structures uniformly distributed in the circumferential direction. The reverse cutting 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.

Further description will be given with reference to fig. 29 to 46, taking a cylinder scheme as an example, a compressor cylinder embodiment configuration will be described in detail.

First embodiment of the cylinder assembly, this embodiment directly employs a two-cylinder scheme of the cylinder scheme. It consists of a static disc and a dynamic disc. The fixed disc cover plate is circular, and two semicircular arc plates with completely equal inner circle sizes are uniformly distributed on a circle taking the center of the fixed disc cover plate as the center of the circle. The outer circle of the semicircular arc plate and the reinforced metal structure are connected into a whole, so that in the embodiment, the outer arc line is hidden in a machine body with the outer circle of the circular arc of the static disc extending. 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 movable disc backboard is circular, and two reverse-cutting circular plates are uniformly distributed on a circle taking the center of the movable disc backboard as the center of the circle. The eccentricity is the revolution distance between the circle center of the movable disc backboard and the circle center of the stationary disc cover plate. As shown in FIG. 43, the non-engagement cambered surfaces of the two reverse cutting circular plates and the semi-circular plate of the static plate are respectively connected with the metal reinforced connecting structure into a whole, so that the reverse cutting circular plates are non-engaged The arc line is hidden in the movable disc arc body. The end part of the reverse cutting circular plate is semicircular. The diameter of the end part of the reverse cutting circular plate is equal to the radial thickness of the circular arc. The maximum 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 reverse cutting circular plate a is connected with the movable disc backboard, and the other end of the reverse cutting circular plate is open, so that the cylinder volume part of the movable disc is in a half-open mode.

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 movable disc reverse-cutting circular plate is the same as that of the static disc semicircular arc plate, the two ends of the movable disc reverse-cutting circular plate are closed by the movable disc cover plate, and the arc-shaped volume formed in the radial direction is closed by two tangential 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 static disc cover plate. The outer circumference of the static disc is fixedly connected with the compressor bracket or the shell, and the connection modes are various according to the situation. The center of the movable disc is provided with a shaft hole which is used for being matched and connected with a translation mechanism, such as a shafting and the like, and the translation mechanism can drive the movable disc to revolve relative to the static disc. The translation mechanism connected and matched with the movable disk is provided with an anti-rotation device. The anti-rotation device adopts the cross slip ring as the technical scheme of the anti-rotation device, so that a key slot for the cross slip ring to slide is arranged on the other circular end surface of the movable disc backboard relative to the reverse cutting circular plate. The scheme is not limited to the cross slip ring scheme, other existing mechanisms with the same function can be adopted, for example, a plurality of parallel small crankshafts are arranged on one side face of the movable disc backboard, one or more small crankshafts with the axial direction parallel to the main shaft can be connected in a matched mode, the other end of each small crankshaft is arranged on the bottom plate or the fixed 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 movable disc anti-self-transmission mechanism can be formed by the small crankshaft, related bearing components and the like, and the other mechanisms are conventional and are not described in detail. But the cross slip ring scheme is the simplest and the lowest in processing cost. The center of the fixed disc 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 fixed disc or does not need to pass through the fixed disc, so that the main shaft can be flexibly determined according to the situation by a person skilled in the art. The central shaft hole of the movable disc can be semi-open or penetrating, also depends on the installation mode, the position and the structural characteristics of the main shaft in the shafting, and the size of the shaft hole is determined according to the size of the main shaft mechanism, thus the movable disc belongs to conventional arrangement and is not repeated here.

As shown in fig. 47 to 56, the movable disc of the cylinder assembly may also be 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 disc only has a semi-circular plate and an extremely supporting and fixing connection part, and no static disc cover plate is arranged at the two axial ends. 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. 57 to 64, the static disc of the cylinder assembly may also be totally enclosed at two axial ends, that is, two axial ends are respectively connected and fixed by a cover plate with the same size, a through hole through which the spindle passes and moves is left in the middle of the cover plate, at this time, the corresponding circular plate of the movable disc is totally open, that is, 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 cover 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 dynamic and static arc strength is reduced when the cover plate and the back plate are fixed, the stability is poor, and the rotation preventing device of the translation mechanism is particularly inconvenient to set.

The reverse cutting circular plate, the semicircular arc plate and the cover plates and the back plates at the two axial ends of the cylinder can be freely combined according to the cylinder scheme and the whole machine design, and the reverse cutting circular plate, the semicircular arc plate and the cover plates and the back plates of the two axial ends of the cylinder belong to coverage areas of the right characteristics of the invention and are not listed one by one.

Air compressor embodiment one:

the compressor is provided with a shell, wherein the shell is cylindrical, the lower end of the cylinder is connected with a bottom plate, and the upper open end of the cylinder is connected with an upper cover through a flange and bolts; the static disc cover plate of the cylinder is mounted close to the inner wall of the upper cover, the cover plate is fixed with the shell by the upper cover of the compressor, and is concentric with the inner circle of the shell cylinder, one end of the static disc cover plate facing the bottom is fixedly connected with an integral semicircular arc plate of the cylinder static disc, the semicircular arc plate is in meshed clearance fit with the movable disc anti-cutting circular plate, and the axial lower end of the anti-cutting circular plate is fixedly connected with the movable disc back plate into a whole; a key groove and a sliding groove for the anti-rotation device to slide are formed in one end face of the movable disc backboard facing the bottom plate and the end face of the bottom plate facing the inner side, the key groove of the movable disc backboard is vertical to the sliding groove space of the bottom plate, and a cross slip ring of the anti-rotation mechanism is arranged between the movable disc backboard and the bottom plate of the shell and is matched with the key groove and the sliding groove; the bottom plate is provided with a lower bearing, and the main shaft penetrates through an upper bearing arranged in the center of the upper cover and a main bearing of the movable disc to be in supporting fit with the lower bearing; and one end of the main shaft of the compressor, which extends out, is connected with the motor through a coupler. The motor is fixedly connected with the upper cover through a motor bracket of the upper cover; the main shaft is an eccentric circle main shaft, the distance between the eccentric circle and the axis of the main shaft is the eccentricity, and the eccentricity is equal to the revolution radius of the movable disc. And the eccentric circle of the main shaft is matched with a main bearing support arranged in the middle of the movable disc. An air inlet is formed in one side of the cylindrical shell; the two air outlets are arranged on the axial direction of the static disc, close to the compression end point of the cylinder, upwards penetrate through the cover plate of the static disc and correspond to the exhaust pipe of the upper cover, and are used for being connected with the one-way exhaust valve and the external pipe fitting.

Air compressor embodiment two:

as shown in fig. 81 to 90, an air compressor employing a double cylinder assembly has a cylindrical casing 2c2, a bottom plate is connected to the lower end of the casing 2c2, and the bottom plate is provided with a chute for cooperation of a cross slip ring for preventing rotation of the translation mechanism. The bottom of the bottom plate is provided with a bracket 2c25. A key groove 2c117 for supporting and matching the cross slip ring is formed in the lower bottom surface of the movable disc backboard, and the sliding groove is vertical to the space of the key groove 2c 117; the cross slip ring is arranged between the bottom plate and the movable plate back plate. The upper part of the movable disc backboard is provided with two reverse-cutting circular plates which are symmetrical with respect to the central point of the movable disc, a connecting structure is arranged between the two reverse-cutting circular plates in the radial direction, and the two reverse-cutting circular plates are integrated. The middle part of the bearing chamber is provided with a bearing chamber, and a center bearing 2c6 is arranged in the bearing chamber. Weight-reducing holes 2c116 and 2c119 are provided as shown in fig. 85 for weight reduction. The reverse cutting circular plate is correspondingly meshed with the semicircular arc plate of the static disc. The upper end of the semicircular arc plate is connected with the cover plate. The cover plate is fixedly connected with the inner wall of the shell in the circumferential direction. The upper top surface of the cover plate is pressed, adhered and fixed with the upper cover 2c 22. The upper cover 2c22 is fixedly connected with the upper end part of the cylinder 2c21 of the shell through flange bolts. The center of the upper cover is provided with an upper bearing 2c5, a crankshaft 2c3 supported by the upper bearing 2c5 penetrates through a penetrating through hole of the fixed disc cover plate, a crankshaft pin 2c34 arranged at the lower end is matched with a center bearing 2c6 arranged at the radial middle position of the movable disc and supported by the bearing, the movable disc is dragged to revolve relative to the fixed disc, and meanwhile, the inverted-tangential circular plate translates relative to the semicircular arc plate. The portion of the crankshaft 2c3 extending out of the upper cover is connected with the motor 2c9 through a coupling. The motor 2c9 is fixedly connected with the upper cover and the shell through a motor bracket arranged on the upper cover. The radial side of the housing is provided with an air inlet 2c24. And an air outlet is arranged at a position, close to the compression end point of the air cylinder, of the static disc in the axial direction, and the two air outlets correspond to the two air cylinders respectively. The two air outlets are led to the outside of the shell through holes 2c23 correspondingly formed in the upper cover, and can be conveniently connected with the one-way exhaust valve and other pipe fittings. The balance structure, the anti-rotation structure and the dynamic and static disk weight reduction structure of the crankshaft are conventional schemes in the technical field and are not described in detail.

Air compressor embodiment three:

as shown in fig. 91 to 107, the compressor of the present embodiment is substantially a double-layer structure of the first embodiment of the air compressor. The double-layer structure is mainly formed by adding a second set of double-cylinder assemblies which are identical to the double-cylinder assemblies in the embodiment of the compressor in the axial direction. The two sets of double-cylinder assemblies share the same eccentric circular main shaft. The two eccentric circular shafts of the eccentric circular main shaft are correspondingly matched with the two layers of movable disks respectively in the axial direction, and the radial direction forms a symmetrical 180-degree angle, so that the radial balance problem of the main shaft and the movable disks is basically solved when the compressor of the embodiment is operated, and additional balance blocks are not needed for radial mass balance arrangement. Because of the double-layer structure of this embodiment, the spindle penetrates through the two layers of the static disc, so as shown in fig. 95 to 100, the static disc is preferably in a split form, and is convenient to disassemble and assemble. The middle-split type static disc is that an integral static disc is divided into two along the maximum distance middle vertical line of the two semicircular arc plates, the two semicircular static discs are symmetrical and are completely attached and butted in the middle, and meanwhile, a sliding groove for the autorotation preventing device to be matched with the cross slip ring is formed in the upper surface of the static disc cover plate of the lower layer. In this embodiment, two cross slip rings are axially arranged, the cross slip ring above is located between the movable disk back plate on the upper layer and the stationary disk cover plate on the lower layer, and the cross slip ring below is located between the movable disk back plate below and the bottom plate. Each layer of cylinder is provided with an air inlet 3c24 and two exhaust pipes 3c29, and the arrangement scheme of the air inlet and the exhaust pipes 3c29 is the same as that of the first embodiment of the air compressor; in contrast, as shown in fig. 91 and 92, the four exhaust ports are each arranged radially. As shown in fig. 96, the exhaust port is radially arranged such that the circular arc plate of the stationary plate is provided with an exhaust port 3c107 near the compression end point of the cylinder. The exhaust hole 3c107 penetrates through the side wall of the semicircular arc plate and the arc wall and is connected with the part attached to the inner wall of the shell in an extending way until being communicated with the exhaust pipe 3c 29. The double-layer shell of this scheme passes through flange bolt fixed connection.

Similarly, three or more layers of compressor schemes can be designed according to the axial multi-layer compressor scheme. 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, and the compressor does not need to be treated too much.

The invention has the positive effects that: the cylinder operation mode and the driving mode of the invention are similar to the scroll compressor, and are all 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 cylinder volume is extremely small, so that the volumetric efficiency is also high, and therefore, the device inherits various advantages of the scroll compressor. However, the advantages of the compressor according to the invention compared with scroll compressors are: 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 movable disc back plate and the fixed disc cover plate can be standard whole circles or standard whole circles, 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 vortex 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 assembly of a 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 protrude the shape and the mating relationship of the core mating member reverse cut circular plate a and the semicircular plate b. Wherein fig. 1 to 7 are schematic diagrams of the structure and operation principle of the single cylinder assembly:

fig. 1 is a schematic view of a front view of a single cylinder assembly, and fig. 2 is a three-dimensional schematic view of fig. 1. Fig. 3 to 7 are schematic views of arc simulation operation of the movable disk 11 and the stationary disk 10 of the single cylinder assembly, wherein fig. 3 is a schematic view of a state in which a tangential point indicated by an arrow of the reverse cut circular plate a is at zero degree, and in this case, in a compression start state, a volume of the air chamber (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 detailing the construction of a single cylinder assembly.

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

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 is a schematic perspective view of the housing 1c2, in which the upper cover 1c22 is omitted for the sake of clarity of the structure of the chute 1c 271; FIG. 20 is a top view of FIG. 19; FIG. 21 is a schematic view of the W-W cross-sectional structure of FIG. 20;

fig. 22 is a schematic perspective view of the cylinder moving plate 1c11 and the cross slip ring 1c 8; FIG. 23 is a schematic top view of FIG. 22; FIG. 24 is a schematic view of the Y-Y cross-sectional structure of FIG. 23;

Fig. 25 is a schematic plan view of the cylinder block 1c11 and the cross slip ring 1c8 mounted in the housing 1c2, with the upper cover 1c22 omitted; FIG. 26 is a schematic view of the V-V cross-sectional structure of FIG. 25; FIG. 27 is a schematic view of the cross-sectional X-X structure of FIG. 26; fig. 28 is a schematic perspective view of the cross slip ring 1c 8.

Fig. 29 to 46 are schematic structural views of an embodiment of the two cylinder assembly scheme:

fig. 29 is a three-dimensional schematic view of an embodiment of the dual cylinder assembly, fig. 30 is a bottom view of 29, fig. 31 is a front view of fig. 29, fig. 32 is A-A cross-sectional view of fig. 31, fig. 33 is B-B cross-sectional view of fig. 31, and fig. 34 is an elevation three-dimensional view of fig. 30; fig. 35 is a three-dimensional schematic view of the stationary plate 10 of the embodiment, fig. 36 is a front view of the stationary plate 10, fig. 37 is a bottom view of fig. 36, fig. 38 is a cross-sectional view taken in the direction of fig. 37D-D, fig. 39 is a cross-sectional view taken in the direction of fig. 37C-C, and fig. 40 is a left side view of fig. 37; fig. 41 is a three-dimensional schematic view of the movable plate 11 of the embodiment, fig. 42 is a front view of the movable plate 11, fig. 43 is a top view of fig. 42, fig. 44 is an E-E sectional view of fig. 43, fig. 45 is an F-F sectional view of fig. 43, and fig. 46 is a top view of fig. 42 in a three-dimensional view;

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 Z-Z 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 d-d 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 of e-e 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. 65 to 80 are schematic structural views of a first embodiment of an air compressor employing a double cylinder assembly including a schematic structural view of constituent components: FIG. 65 is a three-dimensional schematic view of the air compressor, FIG. 66 is a front view of the air compressor, and FIG. 67 is an L-L sectional view of FIG. 66; FIG. 68 is a schematic perspective view of a main shaft of the air compressor; fig. 69 is a three-dimensional structural schematic view of the stationary plate 10 of the air compressor, fig. 70 is an upper elevation three-dimensional view of fig. 69, fig. 71 is a front view of fig. 70, fig. 72 is a cross-sectional view taken in a direction of fig. 71M-M, fig. 73 is a bottom view of fig. 71, and fig. 74 is a cross-sectional view taken in a direction of N-N of fig. 73; fig. 75 is a three-dimensional schematic view of a cylinder moving plate 11 of the air compressor, fig. 76 is an elevation three-dimensional schematic view of fig. 75, fig. 77 is a front view of the moving plate 11, fig. 78 is a bottom view of fig. 77, fig. 79 is an O-O sectional view of fig. 77, and fig. 80 is a P-P sectional view of fig. 78;

fig. 81 to 90 are schematic structural and component views of a second embodiment of an air compressor according to the present invention, in which a crankshaft main shaft is used as a main shaft: FIG. 81 is a three-dimensional schematic view of the embodiment, FIG. 82 is a side view of the embodiment, and FIG. 83 is a Q-Q cross-sectional view of FIG. 82; FIG. 84 is a three-dimensional schematic view of the structure of the crankshaft of this embodiment; fig. 85 is a schematic three-dimensional structure of the movable plate of the embodiment, fig. 86 is an upper elevation three-dimensional view of fig. 85, fig. 87 is a front view of the movable plate, fig. 88 is an R-R sectional view of fig. 87, fig. 89 is a bottom view of fig. 87, and fig. 90 is a top view of fig. 87;

Fig. 91 to 107 are schematic structural diagrams of a third embodiment of the air compressor and schematic structural diagrams of main components, wherein the embodiment has two sets of cylinder assemblies, and two sets of cylinder assemblies are adopted as double cylinder assemblies: fig. 91 is a three-dimensional schematic view of the third embodiment, fig. 92 is an elevation three-dimensional schematic view of fig. 91, fig. 93 is a side view of the third embodiment, and fig. 94 is an S-S cross-sectional view of fig. 93; FIG. 95 is a schematic three-dimensional view of a part of the middle stationary plate in the third embodiment 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. 96 is an upper elevation three-dimensional schematic view of fig. 95, fig. 97 is a front view of the stationary platen, fig. 98 is a T-T cross-sectional view of fig. 97, fig. 99 is a bottom view of fig. 97, and fig. 100 is a top view of fig. 97; fig. 101 is a three-dimensional schematic view of a movable disk according to the third embodiment, fig. 102 is a bottom view of fig. 101, fig. 103 is a top view of fig. 101, fig. 104 is a front view of the movable disk, and fig. 105 is a U-U sectional view of fig. 104; fig. 106 is a schematic view of the three-dimensional structure of the eccentric circle spindle according to the third embodiment, and fig. 107 is a front view of fig. 106.

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. Single cylinder assembly scheme

Detailed description as shown in fig. 1, the semicircular arc compressor cylinder assembly 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 perpendicular to the cover plate. The movable disk 11 is composed of a reverse cut circular plate a and a back plate in the axial direction of the reverse cut circular plate a, and the reverse cut circular plate a is perpendicular to the back plate. 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 sealed air cavity (ab).

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 end face of the reverse cut circular plate a is similar to an S-shape. The center of the backboard is backboard center o2, and the center of the cover board is cover board center o1. The axis of the backboard center o2 is a backboard axis, the axis of the cover board center o1 is a cover board axis, and the cover board axis is parallel to the backboard axis. The back plate 111 moves relative to the cover plate 101 in the following manner: the backboard axis revolves around the cover board axis, and the revolution radius is the distance between the backboard axis and the cover board axis. 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 cut circular plate a relative to the semicircular plate b can change the volume of the air cavity (ab) to complete the actions of air suction, compression and air discharge, and the cycle is performed.

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 semicircular arc line 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 arc wall b1 and the semicircular arc 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 semicircular arc b2 in the semicircular arc plate b is referred to as the arc mating surface diameter of the semicircular arc plate b.

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

The principle of operation of the cylinder assembly is described in detail below in connection with fig. 3 to 7.

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 positioned on the right side with respect to the second semicircular plate, that is, if the left side radius of the reverse-cut circular plate a is small to the right side radius, the movable plate 11 can revolve counterclockwise. Further, since the translational direction of the first single cylinder scheme 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 simulation principle of the scheme 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 the 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 clockwise around the cover plate center o1 for 90 degrees 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 formed in the stationary plate cover plate or the semicircular arc plate b;

In the process that the back plate center o2 continues to revolve clockwise around the cover plate center o1 for 90 degrees in the position of fig. 5 to the position shown in fig. 6, the motion track of the inverted tangential circular plate a relative to the semicircular plate b is shown in fig. 17, the second inner semicircular wall a2 is separated from the inner semicircular wall b1, the second end semicircular wall b2 is separated from the second inner semicircular wall a2, and the air cavity (ab) is in the 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 movement 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, and the air cavity (ab) is reformed into a closed space volume to enter the next compression process.

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 volume compresses and exhausts, and the relatively open space simultaneously sucks air, namely the air suction and compression processes of the air cylinder assembly are synchronous.

2. Double cylinder assembly scheme

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 other cylinder arc structure is formed by rotating the other cylinder arc structure by 180 degrees along the circumferential direction on a certain circle, 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 inverted circular plate a and one semicircular 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 compression starting moment, and at the moment, the lower cylinder arc structure is at the compression ending moment 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 connection H2 is equal to the sum of the diameters of the semicircular midpoint connection H1 and the second inner semicircular wall a2, i.e., the semicircular midpoint connection 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 inverted tangential circular plates a and the two semicircular plates b constitute two cylinder circular arc structures, which are also called cylinder units. 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 tooling structure for the dual cylinder assembly scheme is further described in connection with fig. 29-46 as follows:

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

The double cylinder embodiment of the cylinder 1 of the semi-arc compressor of the present invention, as shown in fig. 29 to 34, is composed of a stationary plate 10 and a movable plate 11. As shown in fig. 35, 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. 38 and 40, 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. The semicircular arc plate b4 is a non-matching surface arc of the cylinder structure, is hidden in the reinforcing and fixing support bodies of the first fixed disc semicircular arc 102 and the second fixed disc semicircular arc 103, and has only theoretical value in the design stage. The cover plate 101 is provided with a shaft hole 104 in the middle, which is a shaft hole through which the spindle 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. 43, the movable plate 11 has a circular back plate 111. Two reverse-cutting circular plates a are uniformly distributed circumferentially around the center of a side surface of the back plate 111, and the structure and arrangement of the two reverse-cutting circular plates a follow the first double-cylinder scheme. The two circular counter-cut plates a are respectively referred to as a first circular counter-cut plate 112 and a second circular counter-cut plate 113, and the first circular counter-cut plate 112 and the second circular counter-cut plate 113 are centrally symmetrical about the back plate center o 2. The 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 111. The first inverse cutting circular plate 112 and the second inverse cutting circular plate 113 are solid bodies, namely are connected into a whole as shown in fig. 43, and the axial heights of the whole are the same, in other words, the surfaces of the first inverse cutting circular plate 112 and the second inverse cutting circular plate 113 which face the center of the back plate 111 and are not matched with the static plate 10 are directly connected into a whole, and the first outer semicircle a5 and part of the second outer semicircle a6 of the inverse cutting circular plate a are hidden in the whole connected with the two inverse cutting circular plates a, so that the method 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; in this embodiment, the end face of the other axial end of the movable disc 11, which is not connected to the back plate 111, is flush, that is, the end plane of the movable disc 11 is provided with a spindle hole 114 with axial depth at the center of the end plane, that is, the center of the cover plate of the movable disc 11. Meanwhile, in order to reduce the weight of the movable disk 11, weight reducing holes 115 are uniformly distributed on a circle with the center of the main shaft hole 114 as the center of the circle. As shown in fig. 45, the cover plate 111 is provided with keyways 116 on the axial end surfaces of the first and second circular counter-cut plates 112 and 113 for mounting cross slip rings that cooperate with the anti-rotation device of the stop disk.

3. Single-layer double-cylinder air compressor

The specific junction scheme is described below in connection with fig. 65 to 80:

as shown in fig. 65, the single-layer double-cylinder air compressor includes a casing 1c2. The housing 1c2 has a cylindrical shape. The housing 1c2 is constituted by an upper cover 1c22, a cylinder 1c21, and a bottom plate 1c27. The lower end of the cylinder 1c21 is connected to the bottom plate 1c27 of the housing. As shown in fig. 67, a rotary shaft through hole and a cylindrical lower bearing chamber are provided in the center of the bottom plate 1c27, a lower bearing 1c7 is mounted in the lower bearing chamber, and a lower bearing cover 1c28 is provided at the bottom of the lower bearing chamber and is screw-fastened to the bottom plate 1c27. As shown in fig. 66, the cylinder wall 1c21 is provided with an air inlet 1c24 penetrating the cylinder wall. The upper end of the cylinder 1c21 is flanged to the upper cover 1c22 of the housing. As shown in fig. 67, a cylinder 1c1 is mounted in a cavity of a housing 1c2, the cylinder 1c1 is formed by a stationary cylinder disk 1c10 and a movable cylinder disk 1c11, and the stationary cylinder disk 1c10 is mounted in a dynamic fit to the lower part of the axis of the stationary cylinder disk 1c11. In the axial direction, the upper cover 1c22 is closely attached to the lower end face thereof with the cylinder static plate 1c10, and the cylinder static plate 1c10 is stationary relative to the upper cover 1c22.

As shown in fig. 69, the cylinder stationary plate 1c10 is provided with a stationary plate cover plate 1c101, and as shown in fig. 67, the stationary plate cover plate 1c101 of the cylinder stationary plate 1c10 is bonded and fixed by a circular inner step at the upper end of the cylinder 1c21 and the lower end face of the housing cover plate 1c 22. As shown in fig. 73, the center of the stationary plate cover plate 1c101 is provided with a shaft hole 1c104. One side of the stationary plate cover plate 1c101 is provided with a first stationary plate half circular arc 1c102 and a second stationary plate half circular arc 1c103, and the first stationary plate half circular arc 1c102 and the second stationary plate half circular arc 1c103 are symmetrically distributed about the center point of the stationary plate cover plate 1c 101.

As shown in fig. 75, the cylinder head 1c11 is configured by connecting a head back plate 1c111, a first cylinder head arc 1c112, a second cylinder head arc 1c113, and a bearing chamber 1c 114. The bearing chamber 1c114 is located at the center of the movable disk back plate 1c111, that is, the bearing chamber 1c114 is located at the center of the entire arc of the movable disk 1c11, and the shaft hole 1c115 is provided at the center of the movable disk back plate 1c 111. As shown in fig. 79, the bearing chamber 1c114 is concentric with the shaft hole 1c115. As shown in fig. 75, the first cylinder movable disc arc 1c112 and the second cylinder movable disc arc 1c113 are located on both sides of the bearing chamber 1c114, respectively, and the first cylinder movable disc arc 1c112 and the second cylinder movable disc arc 1c113 are center-symmetrical with respect to the center of the bearing chamber 1c 114. As shown in fig. 67, the upper cover 1c22 has an upper bearing chamber with a through shaft hole at the center thereof, and an upper bearing 1c5 is mounted in the upper bearing chamber.

The cylinder static disc 1c10 is provided with an exhaust channel, the exhaust channel is composed of an exhaust hole and an exhaust pipe, the exhaust pipe is arranged on the static disc cover plate 1c101 or on the side wall of the cylinder 1c21, the exhaust pipe is communicated with the outside of the shell 1c2, and the inner cavity of the first static disc semicircular arc 1c102 and the inner cavity of the second static disc semicircular arc 1c103 are respectively provided with an exhaust channel for exhausting.

The design scheme of the specific exhaust passage has two kinds:

first, as shown in fig. 69, the other side of the stationary plate cover 1c101 is provided with a first exhaust pipe 1c105 and a second exhaust pipe 1c106. As shown in fig. 73, the stationary plate cover 1c101 is provided with a first vent hole 1c107 and a second vent hole 1c108 in the axial direction. As shown in fig. 74, the first exhaust hole 1c107 is communicated with the first exhaust pipe 1c105 and the inner cavity of the second static disc semicircular arc 1c103, and the second exhaust hole 1c108 is communicated with the second exhaust pipe 1c106 and the inner cavity of the first static disc semicircular arc 1c 102. As shown in fig. 65, the upper cover 1c22 is provided with two circular holes 1c23. The two circular holes 1c23 are respectively correspondingly matched with the first vent hole 1c107 and the second vent hole 1c108.

Second, a first exhaust hole 1c107 is radially arranged on the second stationary plate semicircular arc 1c103, and a second exhaust hole 1c108 is radially arranged on the first stationary plate semicircular arc 1c 102. The first exhaust pipe 1c105 and the second exhaust pipe 1c106 are radially arranged on the side wall of the cylinder 1c21, the first exhaust hole 1c107 and the first exhaust pipe 1c105 are connected into one exhaust passage, and the second exhaust hole 1c108 and the second exhaust pipe 1c106 are connected into the other exhaust passage. The first exhaust hole 1c107 is communicated with the first exhaust pipe 1c105 and the inner cavity of the second static disc semicircular arc 1c103, and the second exhaust hole 1c108 is communicated with the second exhaust pipe 1c106 and the inner cavity of the first static disc semicircular arc 1c 102.

As shown in fig. 76, the end surface of the movable plate back plate 1c111 facing the bottom plate 1c27 is provided with a key groove 1c117. As shown in fig. 19 and 20, a chute 1c271 is provided in the bottom plate 1c 27. Chute 1c271 is located below keyway 1c117 and is spatially perpendicular to both. As shown in fig. 67, a cross slip ring 1c8 is attached to the lower portion of the movable disk back plate 1c 111. As shown in fig. 28, the cross slip ring 1c8 is constituted by a slip ring main body 1c81, an upper slip key 1c82, and a lower slip key 1c 83. The slip ring main body 1c81 is provided with an upper slide key 1c82 and a lower slide key 1c83, and the upper slide key 1c82 and the lower slide key 1c83 are spaced apart by 90 degrees. In order to ensure balanced stress and stable operation, two upper sliding keys 1c82 and two lower sliding keys 1c83 can be arranged on the sliding ring main body 1c81, the two upper sliding keys 1c82 are spaced 180 degrees, the two lower sliding keys 1c83 are spaced 180 degrees, and the upper sliding keys 1c82 and the lower sliding keys 1c83 are spaced 90 degrees. As shown in fig. 22, the slide key 1c82 on the cross slip ring 1c8 is slidably engaged with the key groove 1c117. As shown in fig. 26 and 27, the cross slip ring 1c8 is slidably engaged with the slide groove 1c271 by the slide key 1c 83. The cross slip ring 1c8, the chute 1c271 and the key groove 1c117 are connected to form an anti-rotation device of the stop disc. The cross slip ring 1c8 body is not limited to a circular shape, but may be an elliptical shape or an elliptical shape.

As shown in fig. 67, the motor bracket 1c26 is provided on the upper cover 1c 22. The motor 1c9 is mounted on the motor bracket 1c26. The output shaft of the motor 1c9 is butt-jointed with a main shaft 1c3. The spindle 1c3 is provided with a spindle eccentric circle 1c32. The balance weight 1c4 is arranged on the main shaft 1c3, and the space included angle between the balance weight 1c4 and the eccentric circle 1c32 of the main shaft is 180 degrees. That is, the spindle 1c3 is an eccentric circle spindle, and the lower end of the spindle 1c3 is supported by the lower bearing 1c7 in an oriented manner as seen from below to above with reference to fig. 67, and passes upward through the cross slip ring 1c8 and the shaft hole 1c115, and the spindle eccentric circle 1c32 is engaged with the bearing chamber 1c 114. To reduce friction, the eccentric spindle circle 1c32 may be in supporting engagement with the main bearing 1c6 in the bearing housing 1c 114. The upper spindle 1c3 passes through the static disc cover plate 1c101 and the upper cover 1c22 to be in supporting fit with an upper bearing 1c5 arranged in the upper bearing chamber. A balance block 1c4 is arranged upwards and used for balancing the eccentric mass; the upward upper end is connected with a prime mover through a coupling, and the prime mover in the embodiment is a motor 1c9, namely, the motor 1c9 is fixedly connected with the shell 1c2 through a motor bracket 1c26 arranged on the upper cover 1c 22. The central shaft hole 1c104 of the static disc cover plate 1c101, the upper bearing 1c5 in the middle of the upper cover 1c22 and the lower bearing 1c7 in the middle of the bottom plate 1c27 are concentric.

As shown in fig. 65, the lower portion of the base plate 1c27 is connected to a bottom bracket 1c25 to facilitate the installation of the compressor.

As shown in fig. 76, the two long side surfaces of the key slot 1c117 are provided with elongated bosses 1c118 fixedly connected to the movable disk back plate 1c111, so as to form a sliding key slot 1c117. Alternatively, the key groove 1c117 may be formed directly on the corresponding position of the back plate.

As shown in fig. 19, the bottom plate 1c27 is provided with a strip-shaped block 1c272 side by side, and a chute 1c271 is formed between the two strip-shaped blocks 1c 272. Alternatively, the chute 1c271 may be formed by directly opening at a corresponding position of the bottom plate 1c 27.

The non-mating surfaces or outer side surfaces of the first static disc semicircular arc 1c102 and the second static disc semicircular arc 1c103 of the embodiment of the compressor can be connected or extended to strengthen the fixed machine body, and the outer shape of the machine body is cut 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. To further strengthen the circumferential fixation of the stationary plate 1c10, the stationary plate cover 1c101 is provided with a key groove 1c109 for snap-fixation with a positioning key of the key groove mounting of the cylinder 1c 21.

As shown in fig. 75, in the embodiment of the present compressor, two symmetrical crescent lightening holes 1c116 are provided on the whole arc body formed by connecting the first cylinder movable disc arc 1c112 and the second cylinder movable disc arc 1c113, and the lightening holes are not necessarily circular under the condition of ensuring the strength requirement and the mass balance, and may have various shapes.

When the compressor operates, the motor 1c9 drives the main shaft 1c3 to rotate, the 1c3 drives the inner ring of the main bearing 1c6 to rotate through the eccentric circle 1c32, the outer ring of the main bearing 1c6 is fixedly connected with the movable disc 1c11 of the air cylinder 1c1, so that the movable disc 1c11 receives a circumferential slip driving force from the eccentric circle 1c32 of the main shaft, and the slip radius is the distance between the center of the main shaft and the center of the eccentric circle 1c32, namely the eccentric distance or revolution radius; because the lower part of the movable disc back plate 1c111 is matched and provided with the cross slip ring anti-rotation mechanism, the movable disc 1c11 only revolves around the main shaft 1c3 and cannot rotate, and the cylinder formed by the circular arc of the movable disc and the circular arc matching surface of the static disc is sealed, compressed, exhausted, synchronously sucked and rotated and continuously runs. Because the main shaft is provided with the mass balance block 1c4, the whole machine is balanced and runs stably. The first cylinder movable disc arc 1c112 and the first static disc semi-arc 1c102 are matched to form a cylinder arc structure, the second cylinder movable disc arc 1c113 and the second static disc semi-arc 1c103 form another cylinder arc structure, and the working principles of compression, exhaust, synchronous suction and rotation processes of the two cylinder arc structures are the same as those shown in fig. 10-14.

As shown in fig. 81 to 90, there is another embodiment of the single-layer double-cylinder air compressor, which is compared with the embodiment shown in fig. 65 to 80, and is characterized in that the main shaft adopted by the embodiment is a crankshaft 2c3, so that the crankshaft 2c34 is connected to and matched with a center bearing 2c6 of a movable disc of the cylinder 2c1, the distance between the axis of the crankshaft 2c34 and the axis of a shaft diameter 2c31 of the crankshaft 2c3 is the eccentricity, and the movable disc revolves along a circle with the eccentricity as a radius under the dragging of the crankshaft, and the working principle is the same as that of the previous embodiment; the diameter of the bearing chamber of the movable disc matched with the crank shaft is smaller, so that the weight reducing hole of the whole circular arc machine body is increased, a plurality of layers of round hole weight reducing holes 2c119 are radially arranged besides the crescent weight reducing holes 2c116, and the weight reducing holes are not limited to the above example under the condition of ensuring the strength requirement and the quality balance; the key groove 2c117 at the lower end of the movable disc back plate is an embedded key groove, which is different from the key groove 1c117 constructed by the long-strip boss in the first compressor embodiment; the compressor embodiment has no bottom bearing cover or other discharge holes, so a blow-down hole 2c29 penetrating the shell is added for discharging waste lubricating oil and the like; other structural features and principles are the same as those of the first compressor embodiment, and will not be described again.

4. Double-layer double-cylinder air compressor

As shown in fig. 94, the casing 1c2 of the double-deck double-cylinder air compressor has two cylinders 1c21. The top of the upper cylinder 1c21 is connected to the upper cover 1c22, and the bottom of the lower cylinder 1c21 is connected to the bottom plate 1c27. The cylinder walls of each cylinder 1c21 are respectively provided with an air inlet 1c24 penetrating through the cylinder walls, and the cylinder walls of each cylinder 1c21 are radially provided with a first exhaust pipe 1c105 and a second exhaust pipe 1c106. Two sets of mounting cylinders 1c1 are axially mounted in the housing 1c 2. The spindle 1c3 is provided with two spindle eccentric circles 1c32, the two spindle eccentric circles 1c32 are axially arranged, and the two spindle eccentric circles 1c32 are axially projected at 180-degree intervals. The two eccentric circles 1c32 of the main shaft are each engaged with the bearing chamber 1c114 of one cylinder 1c1. The bottom of each cylinder 1c1 is provided with a set of anti-stop disc rotation device, a chute 1c271 of the upper anti-moving disc rotation device is arranged on a static disc cover plate 1c101 of the lower cylinder 1c1, and a chute 1c271 of the lower anti-moving disc rotation device is arranged on a bottom plate 1c27.

In order to further reduce the production difficulty, as shown in fig. 95 to 100, each cylinder static disc 1c10 is composed of two parts, wherein one part is provided with a first static disc semi-circular arc 1c102, and the other part is provided with a second static disc semi-circular arc 1c103.

The double-layer double-cylinder air compressor is further described with reference to fig. 91 to 107, and in contrast to the single-layer double-cylinder air compressor:

the double-layer double-cylinder air compressor is characterized in that a single-layer cylinder is axially changed into a double-layer cylinder, or a layer of shell and cylinders with the same structural characteristics are additionally arranged at the upper end of the shell of the single-layer double-cylinder air compressor. The two layers of shells are fixedly connected by flange bolts, and a directional chute for sliding fit of the cross slip ring is additionally arranged on the upper surface of the static disc cover plate of the lower layer of air cylinder and is used for matching the revolution of the upper layer of air cylinder moving disc. Referring to fig. 106 or 107, the eccentric circle spindle is provided with two eccentric circles matched with the main bearings of the two cylinder movable disks, and the two eccentric circles axially correspond to the lower cylinder and the upper cylinder respectively and are symmetrical at 180 degrees by taking the spindle axis as the circle center in the radial direction. 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 of the characteristic limitation of the double-layer structure, the axial exhaust of the exhaust port can lead to complex structure, so the exhaust port is set to be radial exhaust, as shown in fig. 96 to 98, the exhaust port 3c107 passes through the semicircular arc of the static disc, and the machine body extending towards the direction of the shell is attached to the exhaust port of the butt joint shell, and obviously, four exhaust ports 3c107 correspond to four exhaust pipes 3c29 of the shell wall of the compressor. Of course, the exhaust hole of the upper cylinder can also be arranged at the top. An air inlet 3c24 is arranged on the shell wall of each layer, and two air inlets 3c24 are shared; for ease of assembly and disassembly of the apparatus, referring to fig. 95-100, the static disk may be bisected in half by the static disk at the symmetrical midline of the two semicircular arcs.

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.

Obviously, the compressor of the invention can compress the conventional gas, can also be used as a pump for conveying high-pressure liquid, and can be used for refrigerating air-conditioning equipment such as air conditioners, refrigerators and the like.

The technical characteristics of the compressor are that the scheme of the semicircular arc 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. The semicircle compressor cylinder subassembly, its characterized in that: the rotary disc comprises a static disc (10) and a movable disc (11), wherein the static disc (10) is composed of a semicircular arc plate (b) and a cover plate (101) in the axial direction of the semicircular arc plate (b), and the movable disc (11) is composed of a reverse cutting circular plate (a) and a back plate (111) in the axial direction of the reverse cutting circular plate (a); the semicircular arc plate (b) is matched with the reverse cutting circular plate (a), 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 sealed air cavity (ab); 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 is a backboard center (o 2), the center of the cover board is a cover board center (o 1), the axis of the backboard center (o 2) is a backboard axis, the axis of the cover board center (o 1) is a cover board axis, and the cover board axis is parallel to the backboard axis; the back plate (111) moves relative to the cover plate (101) in the following movement mode: the backboard axis revolves around the cover plate axis, the revolution radius is the distance between the backboard axis and the cover plate axis, the backboard (111) drives the reverse cutting circular plate (a) to be unchanged in the opening direction of the first semicircular plate and the second semicircular plate in the moving process of the reverse cutting circular plate (a) relative to the semicircular plate (b), and the volume of the air cavity (ab) can be changed by the movement of the reverse cutting circular plate (a) relative to the semicircular plate (b); the cover plate or the semicircular arc plate (b) is provided with an exhaust hole;

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); the curved surface formed by the first outer semicircle (a 5) and the second outer semicircle (a 6) is parallel to the curved surface formed by the first inner semicircle wall (a 1) and the second inner semicircle wall (a 2); 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-arc compressor cylinder assembly of 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-arc compressor cylinder assembly of 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-arc compressor cylinder assembly of claim 1 wherein: the diameter of the second inner semicircular wall (a 2) minus the thickness of the semicircular plate (b) is equal to the revolution diameter of the movable disk (11) when revolving relative to the stationary disk (10).

5. The semi-arc compressor cylinder assembly of claim 2 wherein: the cover plate is provided with two semicircular plates (b), and the two semicircular plates (b) are centrally symmetrical with respect to the center (o 1) of the cover plate; the backboard is provided with two reverse-cutting circular plates (a), and the two reverse-cutting circular plates (a) are centrally symmetrical relative to the center (o 2) of the backboard; the distance between the midpoints of the two first inner semicircular walls (a 1) is a semicircular midpoint connecting line (H1), the distance between the midpoints of the two inner semicircular walls (b 1) is 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 plates (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 plates (b); a circular arc structure of a cylinder is formed by a reverse cutting circular plate (a) and a semicircular arc plate (b) on the same side.

6. The semi-arc compressor cylinder assembly as set forth in claim 5 wherein: the semicircular arc midpoint connecting line (H2) is equal to the diameter 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 arc wall (b 2), namely: h2 =h1+Φ _a2 -Φ _b2 ；

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), namely: h1 Not less than phi _a1 +Φ _a2 +Φ _a3 。

7. The semi-arc compressor cylinder assembly as set forth in claim 5 wherein: the static disc (10) is provided with a circular cover plate (101), two semicircular arc plates (b) are arranged on the same side surface of the cover plate (101), one semicircular arc plate is called a first static disc semicircular arc (102), the other semicircular arc plate (b) is called a second static disc semicircular arc (103), the first static disc semicircular arc (102) and the second static disc semicircular arc (103) are uniformly distributed on a concentric circle of the cover plate (101), one axial end of the first static disc semicircular arc is fixedly connected with the same side surface of the cover plate (101), and the axial heights of the first static disc semicircular arc (102) and the second static disc semicircular arc (103) are the same; the middle part of the cover plate (101) is provided with a shaft hole (104); the movable disc (11) is provided with a circular back plate (111), two reverse cutting circular plates (a) are circumferentially and uniformly distributed by taking the center of one side surface of the back plate (111) as the center, 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 symmetrical about the center (o 2) of the back plate, 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); a spindle hole (114) with axial depth is arranged at the center of the back plate (111); weight reducing holes (115) are uniformly distributed on a circle taking the circle center of the main shaft hole (114) as the circle center; a key groove (116) is arranged on the axial end face of the other side face of the back plate (111).

8. The semi-arc compressor cylinder assembly as set forth in claim 7 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), the axial and radial directions of the movable disc (11) and the static disc (10) are in dynamic clearance fit, and the fit clearance between the tangential points of the axial and radial circular arcs is smaller than 0.1mm.

9. An air compressor incorporating the half arc compressor cylinder assembly of any one of claims 1 to 8, characterized in that: comprises a shell (1 c 2), wherein the shell (1 c 2) is in a cylinder shape, and the shell (1 c 2) consists of an upper cover (1 c 22), a cylinder (1 c 21) and a bottom plate (1 c 27); the lower end of the cylinder (1 c 21) is connected with a bottom plate (1 c 27) of the shell; an air inlet (1 c 24) penetrating through the cylinder wall is arranged on the cylinder wall of the cylinder (1 c 21); an upper cover (1 c 22) is mounted on the upper end of the cylinder (1 c 21); a cylinder (1 c 1) is arranged in a cavity of the shell (1 c 2), the cylinder (1 c 1) is formed by matching a cylinder static disc (1 c 10) with a cylinder dynamic disc (1 c 11), the cylinder static disc (1 c 10) is axially and dynamically matched with the cylinder dynamic disc (1 c 11), the cylinder static disc (1 c 10) is fixedly connected with the shell (1 c 2), and the cylinder static disc (1 c 10) is static relative to the upper cover (1 c 22);

The cylinder static disc (1 c 10) is provided with a static disc cover plate (1 c 101), the center of the static disc cover plate (1 c 101) is provided with a shaft hole (1 c 104), one side of the static disc cover plate (1 c 101) is provided with a first static disc semicircular arc (1 c 102) and a second static disc semicircular arc (1 c 103), the first static disc semicircular arc (1 c 102) and the second static disc semicircular arc (1 c 103) are symmetrically distributed about the center point of the static disc cover plate (1 c 101), the cylinder static disc (1 c 10) is provided with an exhaust channel, the exhaust channel is composed of an exhaust hole and an exhaust pipe, the exhaust pipe is arranged on the static disc cover plate (1 c 101) or on the side wall of the cylinder (1 c 21), and the inner cavity of the first static disc semicircular arc (1 c 102) and the inner cavity of the second static disc semicircular arc (1 c 103) are respectively communicated with one exhaust channel;

the cylinder movable disc (1 c 11) is formed by connecting a movable disc back plate (1 c 111), a first cylinder movable disc arc (1 c 112), a second cylinder movable disc arc (1 c 113) and a bearing chamber (1 c 114), wherein the bearing chamber (1 c 114) is positioned at the center part of the movable disc back plate (1 c 111), a shaft hole (1 c 115) is arranged at the center part of the movable disc back plate (1 c 111), and the bearing chamber (1 c 114) is correspondingly communicated with the shaft hole (1 c 115); the first cylinder moving disc arc (1 c 112) and the second cylinder moving disc arc (1 c 113) are respectively positioned at two sides of the bearing chamber (1 c 114), and the first cylinder moving disc arc (1 c 112) and the second cylinder moving disc arc (1 c 113) are centrally symmetrical with respect to the center of the bearing chamber (1 c 114); an anti-stop disc rotation device is arranged between the cylinder moving disc (1 c 11) and the bottom plate (1 c 27), a first cylinder moving disc arc (1 c 112) and a first static disc semicircular arc (1 c 102) are matched to form a cylinder arc structure, and a second cylinder moving disc arc (1 c 113) and a second static disc semicircular arc (1 c 103) form another cylinder arc structure;

The shell (1 c 2) is provided with a motor (1 c 9), an eccentric driving mechanism is arranged on an output shaft of the motor (1 c 9), and the eccentric driving mechanism is matched with the air cylinder movable disc.

10. An air compressor according to claim 9, wherein: the eccentric driving mechanism consists of a main shaft (1 c 3) and a main shaft eccentric circle (1 c 32), the main shaft eccentric circle (1 c 32) is arranged at the lower part of the main shaft (1 c 3), and the main shaft eccentric circle (1 c 32) is matched with a bearing chamber (1 c 114) of the cylinder movable disc.

11. An air compressor according to claim 9, wherein: the eccentric driving mechanism is composed of a crankshaft (2 c 3) and a crankshaft tip (2 c 34), the crankshaft tip (2 c 34) is arranged at the lower part of the crankshaft (2 c 3), and the crankshaft tip (2 c 34) is matched with a bearing chamber of a cylinder movable disc.

12. An air compressor according to claim 9, wherein: the device for preventing the rotating disc from rotating is formed by matching a cross slip ring (1 c 8), a chute (1 c 271) and a key slot (1 c 117); the end face of the movable disc backboard (1 c 111) facing the bottom plate (1 c 27) is provided with a key groove (1 c 117), the bottom plate (1 c 27) is provided with a sliding groove (1 c 271), the sliding groove (1 c 271) is positioned below the key groove (1 c 117), and the two spaces are vertical; a cross slip ring (1 c 8) is arranged at the lower part of the movable disc backboard (1 c 111); the cross slip ring (1 c 8) is composed of a slip ring main body (1 c 81), an upper sliding key (1 c 82) and a lower sliding key (1 c 83), wherein the upper sliding key (1 c 82) and the lower sliding key (1 c 83) are arranged on the slip ring main body (1 c 81), the upper sliding key (1 c 82) and the lower sliding key (1 c 83) are separated by 90 degrees, and the upper sliding key (1 c 82) of the cross slip ring (1 c 8) is in sliding fit with the key groove (1 c 117); the cross slip ring (1 c 8) is matched with the sliding groove (1 c 271) in a sliding way by a sliding key (1 c 83).

13. An air compressor according to claim 9, wherein: a first exhaust pipe (1 c 105) and a second exhaust pipe (1 c 106) are arranged on one side of the static disc cover plate (1 c 101) corresponding to the upper cover (1 c 22), a first exhaust hole (1 c 107) and a second exhaust hole (1 c 108) are axially formed in the static disc cover plate (1 c 101), the first exhaust hole (1 c 107) and the first exhaust pipe (1 c 105) are connected into an exhaust channel, and the second exhaust hole (1 c 108) and the second exhaust pipe (1 c 106) are connected into another exhaust channel; the first exhaust hole (1 c 107) is communicated with the inner cavities of the first exhaust pipe (1 c 105) and the second fixed disc semicircular arc (1 c 103), and the second exhaust hole (1 c 108) is communicated with the inner cavities of the second exhaust pipe (1 c 106) and the first fixed disc semicircular arc (1 c 102); the upper cover (1 c 22) is provided with two round holes (1 c 23), and the two round holes (1 c 23) are respectively matched with the first exhaust pipe (1 c 105) and the second exhaust pipe (1 c 106) correspondingly.

14. An air compressor according to claim 9, wherein: a first exhaust hole (1 c 107) is radially formed in the second static disc semicircular arc (1 c 103), a second exhaust hole (1 c 108) is radially formed in the first static disc semicircular arc (1 c 102), a first exhaust pipe (1 c 105) and a second exhaust pipe (1 c 106) are radially arranged on the side wall of the cylinder (1 c 21), the first exhaust hole (1 c 107) and the first exhaust pipe (1 c 105) are connected into one exhaust channel, and the second exhaust hole (1 c 108) and the second exhaust pipe (1 c 106) are connected into the other exhaust channel; the first exhaust hole (1 c 107) is communicated with the inner cavities of the first exhaust pipe (1 c 105) and the second fixed disc semicircular arc (1 c 103), and the second exhaust hole (1 c 108) is communicated with the inner cavities of the second exhaust pipe (1 c 106) and the first fixed disc semicircular arc (1 c 102).

15. An air compressor according to claim 14, wherein: the shell (1 c 2) is provided with two cylinders (1 c 21), the top of the upper cylinder (1 c 21) is connected with the upper cover (1 c 22), and the bottom of the lower cylinder (1 c 21) is connected with the bottom plate (1 c 27); an air inlet (1 c 24) penetrating through the cylinder wall is formed in the cylinder wall of each cylinder (1 c 21), and a first exhaust pipe (1 c 105) and a second exhaust pipe (1 c 106) are radially formed in the cylinder wall of each cylinder (1 c 21); two sets of air cylinders (1 c 1) are axially arranged in the shell (1 c 2), two main shaft eccentric circles (1 c 32) are arranged on the main shaft (1 c 3), and the two main shaft eccentric circles (1 c 32) are axially and sequentially arranged; the two eccentric circles (1 c 32) of the main shaft are respectively matched with bearing chambers (1 c 114) of one cylinder (1 c 1); a set of anti-stop disc rotation devices are respectively arranged at the bottom of each cylinder (1 c 1), a sliding groove (1 c 271) of the upper anti-stop disc rotation device is arranged on a static disc cover plate (1 c 101) of the lower Fang Qigang (1 c 1), and a sliding groove (1 c 271) of the lower anti-stop disc rotation device is arranged on a bottom plate (1 c 27).

16. An air compressor according to claim 9, wherein: each cylinder static disc (1 c 10) is composed of two parts, wherein one part is provided with a first static disc semicircular arc (1 c 102), and the other part is provided with a second static disc semicircular arc (1 c 103).

17. An air compressor according to claim 10, wherein: the number of the eccentric circles (1 c 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 (1 c 114); all the eccentric circles (1 c 32) of the main shaft are axially arranged in sequence and are uniformly distributed in the circumferential direction of the main shaft (1 c 3).

18. An air compressor according to claim 17, wherein: the number of the eccentric circles (1 c 32) of the main shaft is three, the axial dimension of the cylinder arc structure of the middle layer is equal to twice the axial dimension of the cylinder arc structures 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.