CN113738648A

CN113738648A - Cylinder component of semi-arc compressor and compressor thereof

Info

Publication number: CN113738648A
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: 2021-12-03
Anticipated expiration: 2041-09-17
Also published as: CN113738643B; CN113653644A; CN113738648B; CN113738643A; CN113775522A; CN113653644B

Abstract

Semicircle compressor cylinder assembly, its characterized in that: the movable disc type; the semicircular arc plate b is matched with the undercut circular plate a, and the semicircular arc plate b and the undercut 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 those of a scroll compressor and are both revolution driving modes. Meanwhile, the moving disc arc and the static disc arc change through tangential motion, so that the volume change of the closed space of the cylinder is achieved, and the purpose of compressing fluid is achieved. Theoretically, the movable disc and the static disc are positioned and supported in the axial direction and the radial direction, contact friction does not occur in the operation process, so the efficiency is high, meanwhile, the compression clearance of the cylinder volume is extremely small, so the volumetric efficiency is high, and therefore, the scroll compressor inherits a plurality of advantages of the scroll compressor.

Description

Cylinder component of semi-arc compressor and compressor thereof

Technical Field

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

Background

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

Disclosure of Invention

In order to solve the above problems, an object of the present invention is to provide a cylinder assembly of a semi-arc compressor and a compressor thereof, which has substantially the same efficiency and vibration as those of a scroll compressor, but the structure of a moving disc and a stationary disc of the cylinder is greatly simplified, and the compression cylinder components of the stationary disc and the moving disc are all composed of semi-circular and circular structures, so that the cylinder assembly is easy to process.

The technical scheme adopted by the invention for solving the technical problems is as follows: the cylinder assembly of the semi-arc compressor comprises a static disc 10 and a dynamic disc 11. The movable disk 11 is composed of 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, which are respectively a full-open static disc, a semi-open static disc and a full-closed static disc:

as shown in fig. 48, the static disc 10 may be formed by only a semicircular arc plate b alone, the semicircular arc plate b may be directly fixed in a casing 1c2 of the air compressor, 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 o 1; the number of the semi-circular arc plates b is two, namely a first static disc semi-circular arc 102 and a second static disc semi-circular arc 103. This is a fully open static disc. The movable plate cooperating with the fully open stationary plate is a fully closed movable plate as shown in fig. 53 and 55, in which a first circular reverse-cut plate 112 and a second circular reverse-cut plate 113 are fixed between two back plates 111. In this state, the semicircular arc plate b and the undercut circular plate a can be matched with the two back plates together to form a sealed air cavity (ab).

As shown in fig. 35, the static disc 10 may also be formed by connecting two semicircular arc plates b and a cover plate 101, wherein the two semicircular arc plates b are respectively a first static disc semicircular arc 102 and a second static disc semicircular arc 103, and the same axial side of the first static disc semicircular arc 102 and the second static disc semicircular arc 103 is connected with the cover plate 101. The semi-open type static disc is matched with a semi-open type movable disc shown in fig. 41, and a back plate 111 is 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 this state, the semicircular arc plate b and the undercut circular plate a can cooperate with the cover plate and the back plate to form a sealed air cavity (ab).

The totally enclosed static disc, as shown in fig. 59 to 62, has two cover plates 101, and a first static disc semi-circular arc 102 and a second static disc semi-circular arc 103 are fixed between the two cover plates 101. Cooperating with the totally enclosed stationary disc is a totally open type movable disc as shown in fig. 63 and 64, and the back plate 111 is located between the first circular plate 112 and the second circular plate 113, and only plays a role in connecting and fixing the two. In this state, the semicircular arc plate b and the undercut circular plate a can cooperate with the two cover plates 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, and can also be in other shapes, when the undercut circular plate a moves relative to the semicircular arc plate b to do work, the semicircular arc plate b can provide supporting force; as shown in fig. 48, the cover plate 101 is only a portion outside the outer semicircular wall b4 of the first stationary disc semi-circular arc 102 and the second stationary disc semi-circular arc 103 for connecting the first stationary disc semi-circular arc 102 and the second stationary disc semi-circular arc 103 with the cylinder housing, and in this embodiment, the first stationary disc semi-circular arc 102 and the second stationary disc semi-circular arc 103 are independent parts. The back plate 111 is a connecting piece for fixing the reverse cutting circular plate a, is usually plate-shaped, and can also be in other shapes, and drives the back plate to drive the reverse cutting circular plate a to work on the semi-circular plate b in the movement mode; as shown in fig. 60 and 63, the back plate 111 is a connecting portion between two circular plates a cut reversely.

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 and one end of a second semicircular plate, the opening directions of the first semicircular plate and the second semicircular plate are opposite, the diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, 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 at the opening of the first semicircular plate, namely the first outer semicircular wall a5, is collinear with the diameter of the inner wall at the opening of the second semicircular plate, namely the second inner semicircular wall a 2. The center of the back plate is the back plate center o2, and the center of the cover plate is the cover plate center o 1. The axis of the back plate center o2 is the back plate axis, the axis of the deck plate center o1 is the deck plate axis, and the deck plate axis is parallel to the back plate axis. As shown in fig. 9 a-14, the deck axis is shown as deck center o1 and the back plate axis is shown as back plate center o 2. 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, and the revolution radius is the distance between the back plate axis and the cover plate axis, also called eccentricity. When 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 an 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 semi-arc plate b is provided with an exhaust hole. Since the back plate axis revolves around the cover plate axis, the movement of the back plate 111 with respect to the cover plate 101 will be referred to as the revolution of the back plate 111 with respect to the cover plate 101 for the convenience of description.

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

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

The sum of the diameters of the first and second inner semi-circular walls a1 and a2 is equal to the sum of the diameters of the inner semi-circular arc wall b1 and the second end semi-circular arc wall b 2.

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

The cover plate is provided with two semicircular arc plates b which are centrosymmetric about a cover plate center o 1; the back plate is provided with two circular reverse-cutting plates a which are centrosymmetric about a back plate center o 2; the distance between the midpoints of the two first inner semicircular walls a1 is a semicircular midpoint connecting line H1, the distance between the midpoints of the two inner semicircular walls b1 is a semicircular arc midpoint connecting line H2, the semicircular midpoint connecting line H1 is parallel to the semicircular arc midpoint connecting line H2, the connecting line of the two end points of the semicircular arc plate b is the width L1, and the semicircular midpoint connecting line H1 and the semicircular arc midpoint connecting line H2 are perpendicular to the connecting line L1 of the two end points of the semicircular arc plate b; and a reverse cutting circular plate a and a semicircular arc plate b on the same side form a cylinder arc structure.

The semi-arc midpoint connecting line H2 is equal to: the semi-circular midpoint connecting line H1 plus the diameter of the second inner semi-circular wall a2 minus the diameter of the second end semi-circular arc wall b 2. Namely: h2 ═ H1+ Φ_a2-Φ_b2. The size relationship is an important guarantee that the moving disc arc and the static disc arc are theoretically tangent without friction when translating according to the set eccentricity.

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

The 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 of the semicircular arc plates is called as a first static disc semicircular arc 102, the other semicircular arc plate b is called as 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 the concentric circle of the cover plate 101, one axial end of the first static disc semicircular arc 102 and one axial end of the second static disc semicircular arc 103 are 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, the circle center of one side surface of the back plate 111 is used as the center, two circular reverse cutting plates a are uniformly distributed in the circumferential direction, the two circular reverse cutting plates a are respectively called a first circular reverse cutting plate 112 and a second circular reverse cutting plate 113, the first circular reverse cutting plate 112 and the second circular reverse cutting plate 113 are centrosymmetric about the center o2 of the back plate, and one axial end of the first circular reverse cutting plate 112 and one axial end of the second circular reverse cutting plate 113 are fixedly connected with the same side surface of the back plate 111; a spindle hole 114 with axial depth is arranged at the circle center of the back plate 111; lightening 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 the axial end surface of the other side surface of the back plate 111.

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

The air compressor for assembling the semi-arc compressor cylinder assembly comprises a shell 1c2, wherein the shell 1c2 can be cylindrical, and the shell 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 the bottom plate 1c27 of the shell; an air inlet 1c24 penetrating through the cylinder wall is arranged on the cylinder wall of the cylinder 1c 21; the upper end part of the cylinder 1c21 is flanged with the upper cover 1c22 of the shell; 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 movable disc 1c11, and the cylinder movable disc 1c11 is installed on the axial lower portion of the cylinder static disc 1c10 in a dynamic matching mode. The cylinder static disc 1c10 is fixedly connected with the housing 1c2, specifically, the upper cover 1c22 can be tightly attached to the lower end surface of the cylinder static disc 1c10 in the axial direction, 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 semi-circular arc 1c102 and a second static disc semi-circular arc 1c 103. The first stationary disk half-arc 1c102 and the second stationary disk half-arc 1c103 are symmetrically distributed about a center point of the stationary disk cover 1c101, which is the cover center o1 described above. An exhaust channel is arranged on the cylinder static disc 1c10 and consists 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 and is communicated with the outside of the shell 1c2, and the inner cavity of the first static disc semi-circular arc 1c102 and the inner cavity of the second static disc semi-circular arc 1c103 are respectively communicated with one exhaust channel.

The cylinder moving plate 1c11 is formed by connecting a moving plate back plate 1c111, a first cylinder moving plate arc 1c112, a second cylinder moving plate arc 1c113, and a bearing chamber 1c 114. The first cylinder cam arc 1c112 and the second cylinder cam arc 1c113 have the same shape as the undercut circular plate a shown in fig. 1, and are each constituted by connecting a first semicircular plate and a second semicircular plate. The bearing chamber 1c114 is positioned at the center part of the movable disc back plate 1c111, the shaft hole 1c115 is arranged at the center part of the movable disc back plate 1c111, and the bearing chamber 1c114 is concentric with the shaft hole 1c115 correspondingly; the first cylinder moving disk arc 1c112 and the second cylinder moving disk arc 1c113 are located on both sides of the bearing chamber 1c114, respectively, and the first cylinder moving disk arc 1c112 and the second cylinder moving disk arc 1c113 are symmetrical with respect to the center of the circle of the bearing chamber 1c 114. A device for preventing the rotation of the movable disc is arranged between the cylinder movable disc 1c11 and the bottom plate 1c 27. A key groove 1c117 is formed in the end surface, facing the bottom plate 1c27, of the movable plate back plate 1c111, a sliding groove 1c271 is formed in the bottom plate 1c27, the sliding groove 1c271 is located below the key groove 1c117, and the two spaces are perpendicular; the lower part of the movable disc back plate 1c111 is provided with a cross slip ring 1c 8; 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 slip ring main body 1c81 is provided with an upper sliding key 1c82 and a lower sliding key 1c83, 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 lower sliding key 1c83 of the cross sliding ring 1c8 is in sliding fit with the sliding groove 1c 271; the cross slip ring 1c8, the sliding groove 1c271 and the key groove 1c117 cooperate to form a device for preventing the rotating disc from rotating. The dynamic disk automatic transmission preventing device can be a cross slip ring automatic transmission preventing device, and can also be other devices with the same function, wherein the devices are composed of a plurality of small crankshafts which are axially parallel to the main shaft and have the same eccentricity as the main shaft. The first cylinder movable disc arc 1c112 and the first static disc semi-circular arc 1c102 are matched to form a cylinder arc structure, and the second cylinder movable disc arc 1c113 and the second static disc semi-circular arc 1c103 form another cylinder arc structure.

The housing 1c2 is provided with a motor 1c9, and referring to fig. 65-68, an eccentric drive mechanism is mounted on the output shaft of the motor 1c 9. The eccentric drive mechanism is engaged with the bearing chamber 1c 114. The specific installation mode of the motor 1c9 is that a motor bracket 1c26 is arranged on the upper cover 1c22, and a motor 1c9 is installed on the motor bracket 1c 26. The eccentric driving mechanism has two modes:

first, as shown in fig. 68, the eccentric drive mechanism is composed of a main shaft 1c3 and a main shaft eccentric circle 1c32, and a main shaft eccentric circle 1c32 is provided below the main shaft 1c 3. As shown in fig. 67, the main shaft eccentric circle 1c32 is fitted into the bearing chamber 1c114 of the cylinder movable plate. The lower part of the main shaft 1c3 is provided with a main shaft eccentric circle 1c32, so the main shaft can be called an eccentric main shaft. A main bearing 1c6 may be installed between the main shaft eccentric circle 1c32 and the bearing housing 1c114 to reduce friction therebetween. The main shaft 1c3 further includes an upper shaft diameter 1c31, a lower shaft diameter 1c33, and a weight reduction hole 1c34 at the time of actual machining.

Secondly, as shown in fig. 84, the eccentric drive mechanism is composed of a crankshaft 2c3 and a crankshaft pin 2c34, and a crankshaft pin 2c34 is provided at the lower part of the crankshaft 2c 3. The distance between the axial center of the crankshaft 2c34 and the axial center of the shaft diameter 2c31 of the crankshaft 2c3 is eccentricity. As shown in fig. 83, the crankshaft pin 2c34 fits into the bearing housing. To reduce friction, a central bearing 2c6 is mounted between the crankshaft pin 2c34 and the bearing housing.

The main shaft 1c3 is provided with a balance weight 1c 4.

Two long side surfaces of the key groove 1c117 are provided with strip-shaped bosses 1c118 which are fixedly connected with the movable disc back plate 1c111 and used for forming a sliding key groove 1c 117. The key slot 1c117 may also be directly formed on the corresponding side of the back plate, and directly processed by a planer or a milling machine, without providing the elongated boss 1c 118.

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 round holes 1c23, and the two round holes 1c23 are respectively correspondingly fitted with the first exhaust pipe 1c105 and the second exhaust pipe 1c 106.

A first exhaust hole 1c107 is radially arranged on the second static disc semi-circular arc 1c103, a second exhaust hole 1c108 is radially arranged on the first static disc semi-circular 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 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 communicates with the inner cavities of the first exhaust pipe 1c105 and the second stationary disc semicircular arc 1c103, and the second exhaust hole 1c108 communicates with the inner cavities of the second exhaust pipe 1c106 and the first stationary disc semicircular arc 1c 102.

The shell 1c2 is provided with two cylinders 1c21 which are stacked axially, the top of the upper cylinder 1c21 is connected with an upper cover 1c22, and the bottom of the lower cylinder 1c21 is connected with a 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 cylinders 1c1 are axially mounted in a shell 1c2, two main shaft eccentric circles 1c32 are arranged on a main shaft 1c3, the two main shaft eccentric circles 1c32 are axially and sequentially arranged, are radially symmetrical about the axis of the main shaft by 180 degrees, and two main shaft eccentric circles 1c32 are respectively matched with a bearing chamber 1c114 of one cylinder 1c 1; the bottom of each cylinder 1c1 is respectively provided with a set of device for preventing the rotation of the movable disc, a chute 1c271 of the device for preventing the rotation of the movable disc at the upper part is arranged on a fixed disc cover plate 1c101 of the cylinder 1c1 at the lower part, and a chute 1c271 of the device for preventing the rotation of the movable disc at the lower part is arranged on a bottom plate 1c 27.

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

As shown in fig. 95 to 100, each of the cylinder static discs 1c10 is composed of two parts, 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 1c 103. Divide into two parts with cylinder quiet dish 1c10 and process the preparation respectively, its processing degree of difficulty and cost are lower, and to the embodiment of multilayer cylinder, the structure is installed and is overhauld more easily in the quiet dish simultaneously.

Further description is as follows:

firstly, the structure of the air cylinder component mainly comprises a semicircular arc plate, another double-external reverse-cutting semicircular arc and cover plates at two ends of the height of the circular arc. The double external reverse cutting semi-circular arc can be called as reverse cutting circular plate for short. The reverse cutting circular plate is composed of two relatively small semicircular arcs which are externally tangent and have the same diameter, and the opening direction of the semicircular arcs is 180 degrees. Because the semicircular arc plate and the reverse cutting circular plate move relatively, the static circular arc is a static disc circular arc, and the moving circular arc is a moving disc circular arc. The movable disc circular arc can be dragged by the driving mechanism, takes the set eccentricity as a radius, revolves around the center of the cover plate, and moves relative to the static disc circular arc, so that the connecting diameter of the static disc circular arc end point and the connecting diameter of the movable disc circular arc end point are always parallel in motion.

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

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

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

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, a point is taken on a diameter perpendicular to a connecting line of two end points of a semicircular arc plate b or on an extension line of the diameter as a circle center of revolution, and the semicircular arc plate b and an undercut circular plate a are rotated by 180 degrees to form two cylinder structures which are 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 which does work in front starts the rotation process, and the whole compressor continuously works in a 360-degree rotation range in a cycle.

Further elaborating with reference to fig. 29 to 46, the structure of the embodiment of the compressor cylinder will be described in detail by taking the cylinder scheme as an example.

In the first embodiment of the cylinder assembly, the present embodiment directly adopts a double-cylinder scheme of a cylinder scheme. It is composed of a static disc and a dynamic disc. The static disc cover plate is circular, and two semicircular arc plates with the inner circle size completely equal are uniformly distributed on a circle taking the circle center of the static disc cover plate as the circle center. The excircle of the semicircular arc plate and the reinforcing metal structure are connected into a whole, so that the excircle arc line is hidden in the machine body extending from the excircle of the circular arc of the stationary disk in the embodiment. The end part of the semicircular arc plate is semicircular. The diameter of the end part of the semicircular arc plate is equal to the radial thickness of the arc. As shown in FIG. 9a, the maximum center distance H2 between the inner circles of the two semicircular arc plates of the static disc is equal to the maximum center distance H1 between the outer circles of the circular plate cut reversely by the movable disc plus the revolution diameter of the movable disc during operation. The revolution diameter is twice the eccentricity. The axial height of the two circular arc plates of the static disc is equal to the axial height of the circular plate reversely cut by the movable disc, so that the static disc and the movable disc can be matched to form a sealed air cavity. The one end and the apron of quiet dish semicircle board height are connected, and the other end is opened, and whole quiet dish cylinder volume part is semi-open.

The movable disc back plate is circular, and two circular plates which are reversely cut are uniformly distributed on a circle taking the circle center of the movable disc back plate as the circle center. The eccentricity is the revolution distance between the circle center of the movable disc back plate and the circle center of the static disc cover plate. As shown in fig. 43, the non-meshing arc surfaces of the two circular reverse cutting plates and the semi-circular arc plate of the static disc are respectively connected with the metal reinforced connecting structure into a whole, so that the arc surfaces of the non-meshing surfaces of the circular reverse cutting plates are hidden in the circular arc machine body of the dynamic disc. The end part of the reverse cutting circular plate is semicircular. The diameter of the end part of the reverse cutting circular plate is equal to the radial thickness of the circular arc. The maximum circular arc center distance H1 between the two circular arc plates facing the inner circle of the semi-circular plate of the static disc is larger than or equal to the sum of the diameters of the first inner semi-circular wall a1, the second inner semi-circular wall a2 and the third end semi-circular wall a3 which form the circular arc plate a of the circular arc plates of the reverse cutting, namely the center distance H1 is more than or equal to phi_a1+Φ_a2+Φ_a3It is apparent that the sum of the diameters of the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a3 is equal to the sum of the diameters of the first end semicircular wall a4, the second outer semicircular wall a5 and the third outer semicircular wall a6, i.e. phi_a1+Φ_a2+Φ_a3＝Φ_a4+Φ_a5+Φ_a6. One end of the height a of the reverse cutting circular plate is connected with the movable disc back plate, and the other end of the reverse cutting circular plate is openAnd opening, so that the volume part of the cylinder of the movable disc becomes a half-open form.

The axial opening parts of the movable disc and the static disc are buckled together, and the axial and radial clearance fit is realized, because the height of the circular plate cut reversely by the movable disc is the same as that of the semi-circular arc plate of the static disc, the cover plates of the passive static discs at two ends are sealed, and the arc volume formed in the radial direction is sealed by two tangent points changed in the translation, so that a relatively sealed air cavity ab is formed, and the space volume of the air cavity ab can be changed circularly, so that the processes of air suction, compression and exhaust are realized during operation. The exhaust port is arranged at the end position close to the arc compression of the static disc, radial exhaust is performed if the exhaust port is radially arranged on the side wall of the semicircular arc plate, and axial exhaust is performed if the exhaust port is arranged on the cover plate of the static disc. The outer circumference of the static disc is fixedly connected with a compressor bracket or a shell, and the connection modes are various and are determined according to actual conditions. The center of the movable disc is provided with a shaft hole for being matched and connected with a translational mechanism, such as a shaft system and the like, and the translational mechanism can drive the movable disc to revolve relative to the static disc. And the translation mechanism connected and matched with the movable disc is internally provided with an anti-rotation device. The anti-rotation device adopts the technical scheme that the cross slip ring is taken as the anti-rotation device, so that a key groove for the cross slip ring to slide is formed in the other circular end face of the movable disc back plate, which is opposite to the reverse cutting circular plate. The anti-rotation device is not limited to a cross slip ring scheme, other existing mechanisms with the same function can be adopted, for example, a plurality of parallel small crankshaft structures can be adopted, one or more small crankshafts parallel to the main shaft in the axial direction can be connected to one side face of the movable disc back plate in a matched mode, the other ends of the small crankshafts are installed on the bottom plate or the static disc in a matched mode, the small crankshafts slightly have the eccentric distances equal to the eccentric distances of the main shaft with the small crankshaft axes, the movable disc anti-rotation device can also form a movable disc with related bearing parts and the like to prevent a self-transmission mechanism, and the anti-rotation device is also provided with other types which are all in conventional arrangement and are not detailed. But the cross slip ring scheme is simplest and the processing cost is lowest. The center of the static disc cover plate can be provided with a through main shaft through hole or not, whether the through main shaft through hole is arranged or not is mainly determined by whether the main shaft of the translation mechanism penetrates through the static disc or not, and the technical personnel can flexibly determine according to the actual situation. The central shaft hole of the dynamic disc can be semi-open type or through type, and also depends on the installation mode and position of the main shaft in the shaft system and the structural characteristics of the whole machine, the size of the shaft hole is also determined according to the size of the main shaft mechanism, the main shaft mechanism belongs to the conventional arrangement, and the details are not repeated.

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

As shown in fig. 57 to 64, the stationary disc of the cylinder assembly may also be a disc whose two axial ends are totally closed, that is, two axial ends are respectively connected and fixed by a cover plate with the same size, a through hole for passing the main shaft and moving is reserved in the middle of the cover plate, and the corresponding circular plate with the movable disc reverse cutting is fully open, that is, there is no back plate at the two axial ends of the circular plate with the movable disc reverse cutting, and only the circular plate with the reverse cutting and the middle thereof are connected and fixed with the fixing structure and the shaft hole. The advantage of this kind of cylinder scheme is that the driving disk quality is light more easily to be processed, and the shortcoming is because the fixed bolster effect that loses the apron, and driving disk backstep circular plate intensity reduces, leads to driving disk translation mechanism's the rotation preventing device setting comparatively complicated simultaneously.

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

The reverse cutting circular plate, the semi-circular arc plate and the back plates of the cover plates at two axial ends of the air cylinder have other combination modes, can be freely combined according to the air cylinder scheme and the design requirement of the whole machine, belong to the coverage range of the characteristics of the invention, and are not listed.

The first embodiment of the air compressor:

the compressor is provided with a shell, 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 a bolt; the static disc cover plate of the air cylinder is installed to be close to the inner wall of the upper cover, the cover plate is fixed to the shell through the upper cover of the compressor and is concentric with the inner circle of the cylinder of the shell, one end, facing the bottom, of the static disc cover plate is connected with an integral semicircular plate fixedly provided with the static disc of the air cylinder, the semicircular plate is meshed with the reverse cutting circular plate of the movable disc in a clearance fit mode, and the axial lower end of the reverse cutting circular plate is connected and fixed with the back plate of the movable disc into a whole; the end surface of the movable disc back plate facing the bottom plate and the end surface of the bottom plate facing the inner side are provided with a key groove and a sliding groove for the anti-rotation device to slide, the key groove of the movable disc back plate is perpendicular to the sliding groove space of the bottom plate, and a cross sliding ring of the anti-rotation mechanism is arranged between the movable disc back plate and the shell bottom plate and 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 matched with the lower bearing in a supporting way; and one end of the compressor main shaft extending 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, the distance between the eccentric circle and the axis of the main shaft is an eccentric distance, and the eccentric distance is equal to the revolution radius of the movable disc. The main shaft eccentric circle 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 number of the air outlets is two, the air outlets are arranged on the axial direction of the static disc and close to the compression end point of the air cylinder, and the air outlets upwards penetrate through the static disc cover plate and correspond to the exhaust pipe of the upper cover and are used for being connected with the one-way exhaust valve and an external pipe.

Air compressor embodiment two:

as shown in fig. 81 to 90, the air compressor using the double cylinder assembly has a cylindrical housing 2c2, and a bottom plate is connected to the lower end of the housing 2c2, and the bottom plate is provided with a sliding groove for matching with a cross slip ring for preventing the translation mechanism from rotating. The bottom of the bottom plate is provided with a bracket 2c 25. A key groove 2c117 for supporting and matching the cross slip ring is formed in the lower bottom surface of the movable disc back plate, and the sliding groove is spatially vertical to the key groove 2c 117; the cross slip ring is arranged between the bottom plate and the movable disc back plate. The upper part of the movable disc back plate is provided with two reversely-cut circular plates which are symmetrical about the center point of the movable disc, the two radially-arranged reversely-cut circular plates are of a connected structure, and the two reversely-cut circular plates are integrated. The middle part of the bearing chamber is provided with a central bearing 2c 6. Lightening holes 2c116 and 2c119 are provided for weight reduction as shown in fig. 85. The reverse cutting circular plate is correspondingly meshed with the semi-circular 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, attached and fixed with the upper cover 2c 22. The upper cover 2c22 is fixedly connected to the upper end of the cylinder 2c21 of the housing by means of flange bolts. The upper cover is provided with an upper bearing 2c5 at the center part, a crankshaft 2c3 supported by the upper bearing 2c5 and penetrating through a through hole of the static disc cover plate is matched with a central bearing 2c6 arranged at the radial middle position of the movable disc through a crankshaft 2c34 arranged at the lower end part and supported by the bearing, the movable disc is dragged to revolve relative to the static disc, and meanwhile, the reversely cut circular plate translates to the semicircular circular plate. The crankshaft 2c3 extends out of the upper cover part and is connected with the motor 2c9 through a coupler. 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 2c 24. And the part of the static disc, which is axially close to the compression end point of the air cylinder, is provided with air outlets, and the two air outlets respectively correspond to the two air cylinders. The two air outlets are respectively led to the outside of the shell through holes 2c23 correspondingly formed in the upper cover, and can be conveniently connected with a one-way exhaust valve and other pipe fittings. Along with the embodiment of the air compressor, the balance structure, the anti-rotation structure and the weight reduction structure of the movable and static discs of the crankshaft are conventional schemes in the technical field, and detailed description is omitted.

Air compressor embodiment three:

as shown in fig. 91 to fig. 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 of the compressor embodiment in the axial direction. The two sets of double-cylinder assemblies share the same eccentric circle main shaft. Two eccentric circles of eccentric circle main shaft correspond the cooperation installation with two-layer movable disk respectively on the axial, and footpath becomes symmetrical 180 degrees angles, and main shaft and the radial balanced problem of movable disk are solved basically when this embodiment compressor operation like this, do not need additionally to add the balancing piece and do radial mass balance and set up. Due to the double-layer structure of the present embodiment, the main shaft penetrates through the two layers of the movable and stationary disks, and therefore, as shown in fig. 95 to 100, the stationary disk is preferably in a midsplit form, which is convenient for assembly and disassembly. The split type static disc is an integral static disc which is divided into two parts along the maximum distance perpendicular bisector of the two semi-circular arc plates, the two semi-static discs are symmetrical, the middle parts of the two semi-static discs are completely jointed and butted, and meanwhile, a sliding groove matched with a cross sliding ring of the anti-rotation device is formed in the upper surface of a static disc cover plate of the lower layer. This embodiment axial is equipped with two cross sliding rings, and the cross sliding ring of top is located between the quiet set of apron of movable disk backplate on upper strata and lower floor, and the cross sliding ring of below is located between movable disk backplate and the bottom plate of below. 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 outlet 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 all arranged radially. As shown in fig. 96, the exhaust ports are radially arranged in such a way that exhaust holes 3c107 are formed in the circular arc plate of the stationary disc near the compression end of the cylinder. The exhaust hole 3c107 penetrates through the side wall of the semicircular arc plate and the part where the arc wall extends, is connected and attached to the inner wall of the shell until being communicated with the exhaust pipe 3c 29. The double-layer shell is fixedly connected through the flange bolts.

Similarly, according to the axial multilayer compressor scheme, a compressor scheme with three or more layers can be designed. If the compressor is a three-layer compressor, the axial dimension of the cylinder arc structure of the middle layer cylinder is two times of the axial dimension of the cylinder arc structures of the upper layer and the lower layer at the two axial sides, and the mass of the middle layer movable disc is two times of the mass of the upper layer movable disc and the lower layer at the two axial sides; the eccentric circular mass centers of the main shafts on the upper layer and the lower layer on the two sides are symmetrical about the mass center of the movable disc in the middle layer in the axial direction; in the radial direction, the eccentric circle of the main shaft in the middle layer is circumferentially symmetrical with the coaxial eccentric circles on two sides in the axial direction by 180 degrees of the axis of the main shaft. The balance of the moving mass of the compressor with the three cylinders in the radial direction and the axial direction can realize natural balance without too much treatment.

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

Drawings

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

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

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

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

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

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

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

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

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

Fig. 19 is a schematic perspective view of the housing 1c2, wherein the upper cover 1c22 is omitted to clearly show the structure of the chute 1c 271; FIG. 20 is a top view of FIG. 19; FIG. 21 is a schematic cross-sectional view of the W-W of FIG. 20;

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

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

Fig. 29 to 46 are schematic structural views of an embodiment of the double 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 FIG. 29, FIG. 31 is a front view of FIG. 29, FIG. 32 is a sectional view taken along line A-A of FIG. 31, FIG. 33 is a sectional view taken along line B-B of FIG. 31, and FIG. 34 is an elevational three-dimensional view of FIG. 30; fig. 35 is a three-dimensional schematic view of the stationary disk 10 of this embodiment, fig. 36 is a front view of the stationary disk 10, fig. 37 is a bottom view of fig. 36, fig. 38 is a sectional view taken along fig. 37D-D, fig. 39 is a sectional view taken along 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 board 11 of the embodiment, FIG. 42 is a front view of the movable board 11, FIG. 43 is a plan view of FIG. 42, FIG. 44 is a sectional view taken along line E-E of FIG. 43, FIG. 45 is a sectional view taken along line F-F of FIG. 43, and FIG. 46 is a three-dimensional view taken at a top angle of FIG. 42;

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

fig. 65 to 80 are schematic structural views of a first embodiment of an air compressor, which employs a dual cylinder assembly, including schematic structural views of constituent parts: 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 a sectional view taken along line L-L of FIG. 66; FIG. 68 is a schematic perspective view of the main shaft of the air compressor; fig. 69 is a three-dimensional structural view of a stationary disk 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 along the direction of M-M of fig. 71, fig. 73 is a bottom view of fig. 71, and fig. 74 is a cross-sectional view taken along the direction of N-N of fig. 73; FIG. 75 is a three-dimensional schematic view of a cylinder rotor plate 11 of the air compressor, FIG. 76 is a three-dimensional schematic view in elevation of FIG. 75, FIG. 77 is a front view of the rotor plate 11, FIG. 78 is a bottom view of FIG. 77, FIG. 79 is a cross-sectional view taken along O-O of FIG. 77, and FIG. 80 is a cross-sectional view taken along P-P of FIG. 78;

fig. 81 to 90 are schematic structural views and schematic component views of a second embodiment of an air compressor according to the present invention, in which a main shaft of the embodiment is a crankshaft 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 cross-sectional view taken along line Q-Q of FIG. 82; FIG. 84 is a three-dimensional schematic view of the crankshaft structure of the embodiment; FIG. 85 is a schematic three-dimensional structure of the movable board of the embodiment, FIG. 86 is an upper elevation three-dimensional view of FIG. 85, FIG. 87 is a front view of the movable board, FIG. 88 is a sectional view taken along line R-R 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 a schematic structural view of a third embodiment of the air compressor and a schematic structural view of main components, and the embodiment has two sets of cylinder assemblies, and the two sets of cylinder assemblies are both double cylinder assemblies: FIG. 91 is a three-dimensional schematic view of the third embodiment, FIG. 92 is a three-dimensional schematic view in elevation of FIG. 91, FIG. 93 is a side view of the third embodiment, and FIG. 94 is a cross-sectional view taken along the line S-S of FIG. 93; fig. 95 is a three-dimensional schematic view of the middle static disc of the third embodiment, which is divided into two parts, wherein the two parts have the same structure and shape, and are spliced into the static disc, and the two parts are symmetrical with respect to the center of the circle of the cover plate; fig. 96 is a three-dimensional schematic view in elevation of fig. 95, fig. 97 is a front view of a stationary disk, fig. 98 is a cross-sectional view taken along the line T-T 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 the cam plate of 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 cam plate, and FIG. 105 is a cross-sectional view taken along line U-U of FIG. 104; fig. 106 is a schematic three-dimensional structure of the principal axis of the eccentric circle of 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 is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the examples given herein without any inventive step, are within the scope of the present invention.

One, single cylinder assembly scheme

In the concrete scheme, as shown in figure 1, the cylinder assembly of the semi-arc compressor comprises a static disc 10 and a movable disc 11. The stationary disk 10 is composed of a semicircular plate b and a cover plate in the axial direction of the semicircular plate b, and the semicircular plate b is perpendicular to the cover plate. The movable plate 11 is composed of a reverse cut circular plate a and a back plate in the axial direction of the reverse cut circular plate a, and the reverse cut circular plate a is perpendicular to the back plate. The cover plate and the back plate are generally circular disks and have the structural shapes of a protruding semicircular arc plate b and a reverse cutting circular plate a, and the cover plate and the back plate are omitted in fig. 1 to 7. The semicircular arc plate b and the circular plate a are matched between the cover plate and the back plate, and the cover plate, the back plate, the semicircular arc plate b and the circular plate a are matched together to form a relatively sealed air cavity (ab).

As shown in fig. 1, the reverse cut circular plate a is formed by connecting one end of a first semicircular plate and one end of a second semicircular plate, and the opening directions of the first semicircular plate and the second semicircular plate are opposite, that is, the opening directions of the first semicircular plate and the second semicircular plate are 180 degrees. The diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, and the diameter of the first semicircular plate is larger than that of the second semicircular plate. The end surface of the reverse cut circular plate a is similar to an S-shape. The center of the back plate is the back plate center o2, and the center of the cover plate is the cover plate center o 1. The axis of the back plate center o2 is the back plate axis, the axis of the deck plate center o1 is the deck plate axis, and the deck plate axis is parallel to the back plate axis. 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, and the revolution radius is the distance between the back plate axis and the cover plate axis. In the process that the back plate 111 drives the inverse-cutting circular plate a to move relative to the semicircular arc plate b, the opening directions of the first semicircular plate and the second semicircular plate are always unchanged, namely, the inverse-cutting circular plate a translates or translates relative to the semicircular arc plate b. The translation of the circular plate a and the semicircular plate b can change the volume of the air cavity (ab) so as to complete the actions of air suction, compression and air exhaust, and the operation is circulated.

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

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

As shown in fig. 1a, the sum of the diameters of the first and second inner semicircular walls a1 and a2 is equal to the sum of the diameters of the inner semicircular arc wall b1 and the semicircular arc line b 2. That is, as can be seen from fig. 1a, the sum of the diameters of the first inner semicircular wall a1 and the second inner semicircular wall a2 in the circular reverse-cut plate a is referred to as the mating surface diameter of the circular reverse-cut plate a, and the sum of the diameters of the inner semicircular arc wall b1 and the semicircular arc line 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 plate 11 when revolving relative to the stationary plate 10. The size relationship determines the matching and sealing of the semi-circular arc b2 end of the cylinder cavity in the revolution process of the movable and static discs.

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

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

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

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

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

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

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

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: when the volume of the dynamic and static arc closed space compresses and exhausts, the relatively open space simultaneously inhales, namely, the air suction and compression processes of the air cylinder assembly are synchronous.

Two, double cylinder assembly scheme

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

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

As shown in fig. 9a, the semi-arc midpoint connection line H2 is equal to the sum of the diameters of the semi-arc midpoint connection line H1 and the second inner semi-circular wall a2, i.e., the semi-arc midpoint connection line H2 is equal to the sum of H1 plus two eccentricities. The semicircular midpoint connecting line H1 is equal to or greater than the sum of the diameters of the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a 3. Namely: h1 is not less than phi_a1+Φ_a2+Φ_a3。

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

The specific processing structure of the double-cylinder assembly scheme is further described with reference to fig. 29 to 46 as follows:

since the compressor cylinder of the present invention is preferably a dual cylinder solution in practice, considering power density and convenience of manufacturing and cost factors, the single cylinder solution and its compressor will not be discussed much. The embodiments of the cylinder are further described below based on the dual cylinder solution of the present invention.

The double cylinder embodiment of the semi-circular compressor cylinder 1 of the present invention, as shown in fig. 29 to 34, consists of a stationary disc 10 and a moving disc 11. As shown in fig. 35, the stationary disc 10 has a circular cover plate 101, and two semicircular arc plates b are provided on the same side surface of the cover plate 101, one of which is referred to as a first stationary disc semicircular arc 102, and the other semicircular arc plate b is referred to as a second stationary disc semicircular arc 103. The first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 are uniformly distributed on the concentric circle of the cover plate 101, and one axial end of the first static disc semi-circular arc and one axial end of the second static disc semi-circular arc are fixedly connected with the same side face of the cover plate 101. As shown in fig. 38 and 40, the first stationary disk half-arc 102 and the second stationary disk half-arc 103 have the same axial height. A first inner semicircle 102b1 of the first stationary disk semicircle 102 and a second inner semicircle 103b1 of the second stationary disk semicircle 103 correspond to the inner semicircle wall b 1; the end semicircular arcs 102b2, 102b3, 103b2 and 103b3 of the first stationary disk semicircular arc 102 and the second stationary disk semicircular arc 103 correspond to the second end semicircular arc wall b2 and the first end semicircular arc wall b 3. The semicircular arc plate b4 is a non-matching surface arc of the cylinder structure, is hidden in the reinforcing and fixed supporting body of the first static disc semicircular arc 102 and the second static disc semicircular arc 103, and only has the theoretical value in the design stage. The cover plate 101 has a shaft hole 104 in the middle for the spindle to pass through. The diameter of the shaft bore 104 is greater than the maximum diameter of the shaft through which the spindle passes, whether or not it needs to pass. As shown in fig. 43, the movable plate 11 has a circular back plate 111. The circle center of one side face of the back plate 111 is used as the center, two circular plates a which are cut reversely are uniformly distributed in the circumferential direction, and the structure and the arrangement of the two circular plates a follow the first double-cylinder scheme. The two circular reverse-cut plates a are referred to as a first circular reverse-cut plate 112 and a second circular reverse-cut plate 113, respectively, and the first circular reverse-cut plate 112 and the second circular reverse-cut plate 113 are centrosymmetric with respect to the back-plate center o 2. One axial ends of the first and second circular reverse-

cut plates

112 and 113 are fixedly connected to the same side surface of the back plate 111. The first circular plate 112 and the second circular plate 113 are solid, that is, they are connected into a whole as shown in fig. 43, and the whole has the same axial height, in other words, the first circular plate 112 and the second circular plate 113 are directly connected into a whole towards the surface of the center of the back plate 111, which is not matched with the stationary disc 10, and the first outer semicircle a5 and the part of the second outer semicircle a6 of the circular plate a are hidden in the whole where the two circular plates a are connected, which is only a theoretical basis for design. The circular arc mating surface semi-circular arcs 112a1 and 113a1 of the movable disk 11 correspond to the first inner semi-circular wall a1 of the single cylinder solution, and the other mating surface semi-circular arcs 112a2 and 113a2 correspond to the second inner semi-circular wall a2 of the single cylinder solution. The circular arc radial end semi-circular arcs 112a3 and 113a3 of the movable disk 11, corresponding to the third end semi-circular wall a3 of the cylinder solution; in the scheme, the moving disc 11 is not connected with the axial other end face of the back plate 111 to be flush, which is called the moving disc 11 circular arc end plane, and the central position of the end plane, namely the circle center position of the cover plate of the moving disc 11, is provided with the spindle hole 114 with axial depth. Meanwhile, in order to reduce the weight of the movable disc 11, lightening holes 115 are uniformly distributed on a circle taking the center of the main shaft hole 114 as the center of a circle. As shown in fig. 45, the axial end surface of the cover plate 111, which is free from the first and second circular reverse-

cut plates

112 and 113, is provided with a key groove 116 for fitting a oldham ring of the moving disc rotation preventing device.

Three-layer and single-layer double-cylinder air compressor

Specific junction schemes are described below in conjunction with fig. 65 to 80:

as shown in fig. 65, the single-layer double cylinder air compressor includes a case 1c 2. The case 1c2 is cylindrical. The case 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 to the bottom plate 1c27 of the housing. As shown in fig. 67, the central portion of the bottom plate 1c27 is provided with a through hole for the rotating shaft and a cylindrical lower bearing chamber, the lower bearing chamber is provided with a lower bearing 1c7 therein, and the bottom of the lower bearing chamber is provided with a lower bearing cover 1c28 which is fixed and closed with the bottom plate 1c27 by bolts. As shown in fig. 66, the cylinder 1c21 has an air inlet 1c24 formed in the wall thereof. The upper end of the cylinder 1c21 is flanged to the upper lid 1c22 of the housing. As shown in fig. 67, a cylinder 1c1 is mounted in a cavity of the housing 1c2, the cylinder 1c1 is formed by a cylinder static plate 1c10 and a cylinder dynamic plate 1c11, and the cylinder dynamic plate 1c11 is mounted in a dynamic fit manner on an axial lower portion of the cylinder static plate 1c 10. In the axial direction, the upper cover 1c22 is fitted with a cylinder stator 1c10 against its lower end face, and the cylinder stator 1c10 is stationary with respect to the upper cover 1c 22.

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

As shown in fig. 75, the cylinder cam plate 1c11 is formed by connecting a cam back plate 1c111, a first cylinder cam plate arc 1c112, a second cylinder cam plate arc 1c113, and a bearing chamber 1c 114. The bearing chamber 1c114 is located at the center of the movable board back plate 1c111, i.e. the bearing chamber 1c114 is located at the center of the circular arc of the movable board 1c11, and the shaft hole 1c115 is provided at the center of the movable board back plate 1c 111. As shown in fig. 79, the bearing chamber 1c114 is concentric with the shaft hole 1c 115. As shown in fig. 75, the first cylinder moving disk arc 1c112 and the second cylinder moving disk arc 1c113 are located on both sides of the bearing chamber 1c114, respectively, and the first cylinder moving disk arc 1c112 and the second cylinder moving disk arc 1c113 are symmetrical about the center of the circle of the bearing chamber 1c 114. As shown in fig. 67, an upper bearing chamber having a through-hole is provided in the center of the upper cover 1c22, 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 semi-circular arc 1c102 and the inner cavity of the second static disc semi-circular arc 1c103 are respectively provided with an exhaust channel for exhaust.

The specific design schemes of the exhaust passage are two types:

first, as shown in fig. 69, the other side of the stationary cover 1c101 is provided with a first exhaust pipe 1c105 and a second exhaust pipe 1c 106. As shown in fig. 73, the stationary cover plate 1c101 is provided with a first exhaust hole 1c107 and a second exhaust hole 1c108 in the axial direction. As shown in fig. 74, the first exhaust hole 1c107 communicates with the inner cavity of the first exhaust pipe 1c105 and the inner cavity of the second semicircular disc 1c103, and the second exhaust hole 1c108 communicates with the inner cavity of the second exhaust pipe 1c106 and the inner cavity of the first semicircular disc 1c 102. As shown in fig. 65, the upper cover 1c22 is provided with two circular holes 1c 23. The two circular holes 1c23 are respectively correspondingly fitted with the first discharge hole 1c107 and the second discharge hole 1c 108.

Second, a first exhaust hole 1c107 is radially arranged on the second static disc semi-circular arc 1c103, and a second exhaust hole 1c108 is radially arranged on the first static disc semi-circular arc 1c 102. The side wall of the cylinder 1c21 is provided with a first exhaust pipe 1c105 and a second exhaust pipe 1c106 in the radial direction, 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 cavity of the first exhaust pipe 1c105 and the inner cavity of the second semi-circular arc 1c103 of the static disc, and the second exhaust hole 1c108 is communicated with the inner cavity of the second exhaust pipe 1c106 and the inner cavity of the first semi-circular arc 1c102 of the static disc.

As shown in fig. 76, the end surface of the movable board back plate 1c111 facing the bottom plate 1c27 is provided with a key groove 1c 117. As shown in fig. 19 and 20, the bottom plate 1c27 is provided with a chute 1c 271. The sliding groove 1c271 is positioned below the key groove 1c117, and the two spaces are vertical. As shown in FIG. 67, a cross slip ring 1c8 is mounted on the lower portion of the movable plate back plate 1c 111. As shown in fig. 28, the oldham ring 1c8 is composed of a ring main body 1c81, an upper slider key 1c82, and a lower slider key 1c 83. The slip ring 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 at 90 degrees. In order to ensure stress balance 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 separated by 180 degrees, the two lower sliding keys 1c83 are separated by 180 degrees, and the upper sliding key 1c82 and the lower sliding key 1c83 are separated by 90 degrees. As shown in fig. 22, the sliding key 1c82 of the oldham ring 1c8 is slidably fitted in the key groove 1c 117. As shown in fig. 26 and 27, the slide key 1c83 is slidably fitted to the slide groove 1c271 of the oldham ring 1c 8. The cross slip ring 1c8, the sliding groove 1c271 and the key groove 1c117 are connected to form a device for preventing the rotating disc from rotating. The cross slip ring 1c8 is not limited to a circular shape, and may be an elliptical or elliptical-like shape.

As shown in fig. 67, the upper cover 1c22 is provided with a motor support 1c 26. The motor bracket 1c26 is provided with a motor 1c 9. The output shaft of the motor 1c9 is butt-jointed with a main shaft 1c 3. The main shaft 1c3 is provided with a main shaft eccentric circle 1c 32. The main shaft 1c3 is provided with a balance weight 1c4, and the space included angle between the balance weight 1c4 and the main shaft eccentric circle 1c32 is 180 degrees. That is, the main shaft 1c3 is an eccentric circular main shaft, and referring to fig. 67, as viewed from below, the lower end of the main shaft 1c3 is supported by the lower bearing 1c7, and passes upward through the oldham ring 1c8 and the shaft hole 1c115, and the main shaft eccentric circle 1c32 engages with the bearing chamber 1c 114. To reduce friction, the main shaft eccentric circle 1c32 may be in supporting engagement with the main bearing 1c6 in the bearing housing 1c 114. The upper main shaft 1c3 penetrates through the static cover plate 1c101 and the upper cover 1c22 to support and match with an upper bearing 1c5 arranged in the upper bearing chamber. A balance weight 1c4 is mounted upward to balance the eccentric mass; the motor 1c9 is a motor of this embodiment, that is, the motor 1c9 is fixedly connected to the housing 1c2 via a motor bracket 1c26 provided 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 all concentric.

As shown in FIG. 65, the bottom plate 1c27 is connected to a bottom bracket 1c25 at the lower part thereof to facilitate the installation of the compressor.

As shown in FIG. 76, the key slot 1c117 has elongated bosses 1c118 on both long sides to connect with the movable plate back plate 1c111 for forming a sliding key slot 1c 117. Alternatively, the key slot 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 bar-shaped blocks 1c272 in parallel, and a sliding groove 1c271 is formed between the two bar-shaped blocks 1c 272. Alternatively, the sliding groove 1c271 may be directly formed at a corresponding position of the bottom plate 1c 27.

The non-matching surfaces or outer side surfaces of the first static disc semi-circular arc 1c102 and the second static disc semi-circular arc 1c103 of the embodiment of the compressor can be connected or extended to strengthen and fix the machine body, and under the condition of meeting the requirement of strength design, the appearance of the machine body is cut, and the parts of the machine body are straight plates and are not necessarily made into circular arcs. To further enhance the circumferential fixation of the stationary disc 1c10, the stationary disc cover plate 1c101 is provided with a key slot 1c109 for snap-fitting with a key of the key slot mounting of the cylinder 1c 21.

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

When the compressor runs, the motor 1c9 drives the main shaft 1c3 to rotate, the main bearing 1c6 inner ring is driven to rotate by the 1c3 through the eccentric circle 1c32, the main bearing 1c6 outer ring is fixedly connected with the movable disc 1c11 of the cylinder 1c1, therefore, the movable disc 1c11 is subjected to circumferential sliding and rotating pushing force from the main shaft eccentric circle 1c32, and the sliding and rotating radius of the movable disc is the distance between the axis of the main shaft and the circle center of the eccentric circle 1c32, namely the eccentric distance or the revolution radius; because the lower part of the movable disc back plate 1c111 is provided with the cross slip ring anti-rotation mechanism in a matching way, the movable disc 1c11 only does revolution motion around the main shaft 1c3 and can not rotate, thus ensuring that a cylinder formed by matching surfaces of the movable disc arc and the static disc arc is closed, compressed, exhausted, synchronously sucked and rotated and continuously operated. Because the main shaft is provided with the mass balance block 1c4, the whole machine is balanced and operates smoothly. The first cylinder movable disc arc 1c112 and the first stationary disc semi-circular arc 1c102 are matched to form a cylinder arc structure, the second cylinder movable disc arc 1c113 and the second stationary disc semi-circular arc 1c103 form another cylinder arc structure, and the working principle of the compression, exhaust, synchronous suction and rotation processes of the two cylinder arc structures is the same as that shown in fig. 10 to 14.

As shown in fig. 81 to 90, the single-deck double-cylinder air compressor has another embodiment, which is characterized in that compared with the embodiment shown in fig. 65 to 80, the main shaft adopted by the embodiment is the crankshaft 2c3, so the crankshaft 2c34 is connected with the central bearing 2c6 of the movable disk of the matching cylinder 2c1, the distance between the axis of the crankshaft 2c34 and the axis of the shaft diameter 2c31 of the crankshaft 2c3 is the eccentricity, the movable disk revolves along the circle with the eccentricity as the radius under the dragging of the crankshaft, and the working principle is the same as the previous embodiment; the diameter of a bearing chamber of the movable disc matched with the crankshaft is smaller, so that lightening holes of the whole arc engine body are increased, besides the crescent lightening holes 2c116, a plurality of layers of round hole lightening holes 2c119 are radially arranged, and under the condition of ensuring the strength requirement and the mass balance, the lightening holes are not limited to the example; the key slot 2c117 at the lower end of the movable plate back plate in the embodiment is an embedded key slot, which is different from the way of constructing the key slot 1c117 by the long strip boss in the first compressor embodiment; the compressor has no bottom bearing cover or other discharge holes, so the blow-off hole 2c29 penetrating the shell is added for discharging waste lubricating oil and the like; the rest parts are consistent with the structural features and principles of the first compressor embodiment and are not described in detail.

Four-layer and double-layer double-cylinder air compressor

As shown in fig. 94, the housing 1c2 of the double-deck double cylinder air compressor has two cylinders 1c 21. 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. The wall of each cylinder 1c21 is provided with an air inlet 1c24 penetrating through the wall, and the wall of each cylinder 1c21 is provided with a first exhaust pipe 1c105 and a second exhaust pipe 1c106 in the radial direction. Two sets of mounting cylinders 1c1 are axially mounted within the housing 1c 2. The main shaft 1c3 is provided with two main shaft eccentric circles 1c32, the two main shaft eccentric circles 1c32 are axially arranged, and the two main shaft eccentric circles are projected and spaced by 180 degrees in the axial direction. The two main shaft eccentric circles 1c32 are fitted to the bearing chambers 1c114 of one cylinder 1c1, respectively. The bottom of each cylinder 1c1 is respectively provided with a set of device for preventing the rotation of the movable disc, a chute 1c271 of the device for preventing the rotation of the movable disc at the upper part is arranged on a fixed disc cover plate 1c101 of the cylinder 1c1 at the lower part, and a chute 1c271 of the device for preventing the rotation of the movable disc at the lower part is arranged on a bottom plate 1c 27.

In order to further reduce the production difficulty, as shown in fig. 95 to 100, each of the cylinder static discs 1c10 is composed of two parts, 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 1c 103.

Referring to fig. 91 to 107, the double-deck double-cylinder air compressor will be further explained in comparison with the single-deck double-cylinder air compressor:

the double-layer double-cylinder air compressor is characterized in that a single-layer cylinder is changed into a double-layer cylinder in the axial direction, or a layer of shell and a cylinder with the same structural characteristics are additionally arranged at the upper end of a shell of the single-layer double-cylinder air compressor. The two layers of shells are fixedly connected through flange bolts, and the upper surface of the static plate cover plate of the lower layer of air cylinder is additionally provided with a sliding groove for the sliding fit of the cross sliding ring for matching the revolution of the movable plate of the upper layer of air cylinder. Referring to fig. 106 or fig. 107, the eccentric circle main shaft is provided with two eccentric circles matched with the main bearings of the two cylinder moving disks, the two eccentric circles axially correspond to the lower layer cylinder and the upper layer cylinder respectively, and the two eccentric circles are radially symmetrical by 180 degrees by taking the shaft center of the main shaft as the center of a circle. The radial mass symmetry of the double-layer eccentric circle main shaft can basically achieve natural balance, so that a mass balance block with a larger volume is not arranged. Because of the characteristic limitation of the double-layer structure, the axial exhaust of the exhaust port leads to a complicated structure, so the exhaust port is designed to be radial exhaust, as shown in fig. 96 to 98, the exhaust hole 3c107 passes through the semi-circular arc of the static disc and is jointed with the exhaust port of the butt joint shell along the machine body extending towards the shell direction, obviously, four exhaust holes 3c107 correspond to four exhaust pipes 3c29 on the wall of the shell of the compressor. Of course the exhaust port of the upper cylinder may also be provided at the top. The wall of the shell body of each layer is provided with an air inlet 3c24, and the total number of the air inlets 3c24 is two; to facilitate assembly and disassembly of the device, the stationary disc may be bisected at a median line of symmetry of the arc of the two halves, see fig. 95 to 100.

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

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

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

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

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

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

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

Claims

1. Semicircle compressor cylinder assembly, its characterized in that: the movable disc type; 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 and one end of a second semicircular plate, the opening directions of the first semicircular plate and the second semicircular plate are opposite, the diameter of the first semicircular plate is collinear with the diameter of the second semicircular plate, and the diameter of the first semicircular plate is larger than or equal to the diameter of the second semicircular plate; the center of the back plate is a back plate center o2, the center of the cover plate is a cover plate center o1, the axis of the back plate center o2 is a back plate axis, the axis of the cover plate center o1 is a cover plate axis, and the cover plate axis is parallel to the back plate axis; the back plate 111 moves relative to the cover plate 101 in the following manner: the axis of the back plate revolves around the axis of the cover plate, the revolution radius is the distance between the axis of the back plate and the axis of the cover plate, the opening direction of the first semicircular plate and the opening direction of the second semicircular plate are unchanged in the process that the back plate 111 drives the reverse cutting circular plate a to move relative to the semicircular plate b, and the volume of an air cavity (ab) can be changed by the reverse cutting circular plate a to move relative to the semicircular plate b; the cover plate or the semi-arc plate b is provided with an exhaust hole.

2. The semi-circular compressor cylinder assembly of claim 1, wherein: the first semi-circular plate has three side faces which are respectively a first inner semi-circular wall a1, a fourth end semi-circular wall a4 and a first outer semi-circular wall a 5; the second semicircular plate has three sides which are respectively a second inner semicircular wall a2, a third end semicircular wall a3 and a second outer semicircular wall a 6; the first inner semicircular wall a1 is connected to and tangent to the second inner semicircular wall a2, and the first outer semicircular wall a5 is connected to and tangent to the second outer semicircular wall a 6; the curved surface formed by the first outer semicircle a5 and the second outer semicircle a6 is parallel to the curved surface formed by the first inner semicircle wall a1 and the second inner semicircle wall a 2; two ends of the third end semicircular wall a3 are respectively connected with two ends of the second inner semicircular wall a2 and the second outer semicircular wall a6, and two ends of the fourth end semicircular wall a4 are respectively connected with two ends of the first inner semicircular wall a1 and the first outer semicircular wall a 5.

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

4. The semi-circular compressor cylinder assembly of claim 3, wherein: the sum of the diameters of the first and second inner semi-circular walls a1 and a2 is equal to the sum of the diameters of the inner semi-circular arc wall b1 and the second end semi-circular arc wall b 2.

5. The semi-circular compressor cylinder assembly of claim 2, wherein: the diameter of the second inner semicircular wall a2 minus the thickness of the semicircular arc plate b is equal to the revolution diameter of the movable plate 11 when revolving relative to the stationary plate 10.

6. The semi-circular compressor cylinder assembly of claim 3, wherein: the cover plate is provided with two semicircular arc plates b which are centrosymmetric about a cover plate center o 1; the back plate is provided with two circular reverse-cutting plates a which are centrosymmetric about a back plate center o 2; the distance between the midpoints of the two first inner semicircular walls a1 is a semicircular midpoint connecting line H1, the distance between the midpoints of the two inner semicircular walls b1 is a semicircular arc midpoint connecting line H2, the semicircular midpoint connecting line H1 is parallel to the semicircular arc midpoint connecting line H2, the connecting line of the two end points of the semicircular arc plate b is L1, and the semicircular midpoint connecting line H1 and the semicircular arc midpoint connecting line H2 are perpendicular to the connecting line L1 of the two end points of the semicircular arc plate b; and a reverse cutting circular plate a and a semicircular arc plate b on the same side form a cylinder arc structure.

7. The semi-circular compressor cylinder assembly of claim 6, wherein: the semi-circular arc midpoint connection H2 is equal to the semi-circular midpoint connection H1 plus the diameter of the second inner semi-circular wall a2 minus the diameter of the second end semi-circular arc wall b 2. Namely: h2 ═ H1+ Φ_a2-Φ_b2；

The semicircular midpoint connecting line H1 is equal to or greater than the sum of the diameters of the first inner semicircular wall a1, the second inner semicircular wall a2 and the third end semicircular wall a 3. Namely: h1 is not less than phi_a1+Φ_a2+Φ_a3。

8. The semi-circular compressor cylinder assembly of claim 6, 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 of the semicircular arc plates is called as a first static disc semicircular arc 102, the other semicircular arc plate b is called as 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 the concentric circle of the cover plate 101, one axial end of the first static disc semicircular arc 102 and one axial end of the second static disc semicircular arc 103 are 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 plate 11 is provided with a circular back plate 111, the circle center of one side surface of the back plate 111 is used as a center, two circular reverse cutting plates a are uniformly distributed in the circumferential direction, the two circular reverse cutting plates a are respectively called a first circular reverse cutting plate 112 and a second circular reverse cutting plate 113, the first circular reverse cutting plate 112 and the second circular reverse cutting plate 113 are centrosymmetric about a back plate center o2, and one axial end of the first circular reverse cutting plate 112 and one axial end of the second circular reverse cutting plate 113 are fixedly connected with the same side surface of the back plate 111; a spindle hole 114 with axial depth is arranged at the circle center of the back plate 111; lightening 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 the axial end surface of the other side surface of the back plate 111.

9. The semi-circular compressor cylinder assembly of claim 8, wherein: the axial height of the first inverse cutting circular plate 112 and the second inverse cutting circular plate 113 of the movable disc 11 is equal to the axial height of the first static disc semi-circular arc 102 and the second static disc semi-circular arc 103 of the static disc 10, the movable disc 11 and the static disc 10 are both in dynamic clearance fit in the axial and radial directions, and the fit clearance of the tangent points of the axial and radial circular arcs is less than 0.1 mm.

10. An air compressor incorporating a semi-circular compressor cylinder assembly according to any one of claims 1 to 9, wherein: comprises a shell 1c2, wherein the shell 1c2 is cylindrical, and the shell 1c2 comprises an upper cover 1c22, a cylinder 1c21 and a bottom plate 1c 27; the lower end of the cylinder 1c21 is connected with the bottom plate 1c27 of the shell; an air inlet 1c24 penetrating through the cylinder wall is arranged on the cylinder wall of the cylinder 1c 21; an upper cover 1c22 is mounted on the upper end of the cylinder 1c 21; an air cylinder 1c1 is installed in a cavity of a shell 1c2, the air cylinder 1c1 is formed by matching an air cylinder static disc 1c10 and an air cylinder movable disc 1c11, the air cylinder static disc 1c10 is axially and dynamically matched with an air cylinder movable disc 1c11, the air cylinder static disc 1c10 is fixedly connected with the shell 1c2, and the air cylinder static disc 1c10 is static relative to an 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, one side of the static disc cover plate 1c101 is provided with a first static disc semi-circular arc 1c102 and a second static disc semi-circular arc 1c103, the first static disc semi-circular arc 1c102 and the second static disc semi-circular arc 1c103 are symmetrically distributed about the center point of the static disc cover plate 1c101, the cylinder static disc 1c10 is provided with an exhaust passage, the exhaust passage 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, and the inner cavity of the first static disc semi-circular arc 1c102 and the inner cavity of the second static disc semi-circular arc 1c103 are respectively communicated with one exhaust passage;

the cylinder movable disc 1c11 is formed by connecting a movable disc back plate 1c111, a first cylinder movable disc arc 1c112, a second cylinder movable disc arc 1c113 and a bearing chamber 1c114, wherein the bearing chamber 1c114 is positioned at the center part of the movable disc back plate 1c111, a shaft hole 1c115 is arranged at the center part of the movable disc back plate 1c111, and the bearing chamber 1c114 is correspondingly communicated with the shaft hole 1c 115; the first cylinder movable disc arc 1c112 and the second cylinder movable disc arc 1c113 are respectively positioned at two sides of the bearing chamber 1c114, and the first cylinder movable disc arc 1c112 and the second cylinder movable disc arc 1c113 are symmetrical about the center of the bearing chamber 1c 114; a device for preventing the moving disc from rotating is arranged between the cylinder moving disc 1c11 and the bottom plate 1c27, the first cylinder moving disc arc 1c112 and the first static disc semi-arc 1c102 are matched to form a cylinder arc structure, and the second cylinder moving disc arc 1c113 and the second static disc semi-arc 1c103 form another cylinder arc structure;

the shell 1c2 is provided with a motor 1c9, and an output shaft of the motor 1c9 is provided with an eccentric driving mechanism which is matched with a cylinder moving disc.

11. The air compressor of claim 10, wherein: the eccentric driving mechanism is composed of a main shaft 1c3 and a main shaft eccentric circle 1c32, a main shaft eccentric circle 1c32 is arranged at the lower part of the main shaft 1c3, and the main shaft eccentric circle 1c32 is matched with a bearing chamber 1c114 of a cylinder driving disc.

12. The air compressor of claim 10, wherein: the eccentric driving mechanism is composed of a crankshaft 2c3 and a crankshaft tip 2c34, the lower part of the crankshaft 2c3 is provided with the crankshaft tip 2c34, and the crankshaft tip 2c34 is matched with a bearing chamber of a cylinder driving disc.

13. The air compressor of claim 10, wherein: the device for preventing the rotating disc from rotating is formed by matching a cross slip ring 1c8, a sliding groove 1c271 and a key groove 1c 117; a key groove 1c117 is formed in the end surface, facing the bottom plate 1c27, of the movable plate back plate 1c111, a sliding groove 1c271 is formed in the bottom plate 1c27, the sliding groove 1c271 is located below the key groove 1c117, and the two spaces are perpendicular; the lower part of the movable disc back plate 1c111 is provided with a cross slip ring 1c 8; 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 slip ring main body 1c81 is provided with an upper sliding key 1c82 and a lower sliding key 1c83, 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 lower sliding key 1c83 of the cross sliding ring 1c8 is in sliding fit with the sliding groove 1c 271.

14. The air compressor of claim 10, wherein: 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 round holes 1c23, and the two round holes 1c23 are respectively correspondingly fitted with the first exhaust pipe 1c105 and the second exhaust pipe 1c 106.

15. The air compressor of claim 10, wherein: a first exhaust hole 1c107 is radially arranged on the second static disc semi-circular arc 1c103, a second exhaust hole 1c108 is radially arranged on the first static disc semi-circular 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 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 communicates with the inner cavities of the first exhaust pipe 1c105 and the second stationary disc semicircular arc 1c103, and the second exhaust hole 1c108 communicates with the inner cavities of the second exhaust pipe 1c106 and the first stationary disc semicircular arc 1c 102.

16. The air compressor of claim 15, wherein: the shell 1c2 is provided with two cylinders 1c21, the top of the upper cylinder 1c21 is connected with an upper cover 1c22, and the bottom of the lower cylinder 1c21 is connected with a bottom plate 1c 27; the wall of each cylinder 1c21 is provided with an air inlet 1c24 penetrating through the wall, and the wall of each cylinder 1c21 is radially provided with a first exhaust pipe 1c105 and a second exhaust pipe 1c 106; two sets of cylinders 1c1 are axially mounted in a shell 1c2, two main shaft eccentric circles 1c32 are arranged on a main shaft 1c3, and the two main shaft eccentric circles 1c32 are axially and sequentially arranged; the two main shaft eccentric circles 1c32 are respectively matched with the bearing chamber 1c114 of one cylinder 1c 1; the bottom of each cylinder 1c1 is respectively provided with a set of device for preventing the rotation of the movable disc, a chute 1c271 of the device for preventing the rotation of the movable disc at the upper part is arranged on a fixed disc cover plate 1c101 of the cylinder 1c1 at the lower part, and a chute 1c271 of the device for preventing the rotation of the movable disc at the lower part is arranged on a bottom plate 1c 27.

17. The air compressor of claim 10, wherein: each cylinder static disc 1c10 is composed of two parts, wherein one part is provided with a first static disc semicircle 1c102, and the other part is provided with a second static disc semicircle 1c 103.

18. The air compressor of claim 10, wherein: the number of the main shaft eccentric circles 1c32 is two, three, four or more, and the number thereof is the same as that of the bearing chambers 1c 114; all the main shaft eccentric circles 1c32 are axially arranged in sequence and are uniformly distributed in the circumferential direction of the main shaft 1c 3.

19. The air compressor of claim 18, wherein: the number of the spindle eccentric circles 1c32 is three, the axial size of the cylinder arc structure of the middle layer is twice of the axial size of the cylinder arc structures of the upper layer and the lower layer on the two sides in the axial direction, and the mass of the movable disc of the middle layer is twice of the mass of the movable disc of the upper layer and the lower layer on the two sides in the axial direction; in the axial direction, the mass center of the main shaft eccentric circle of the upper layer and the lower layer at the two ends is symmetrical to the mass center of the middle movable disc; in the radial direction, the eccentric circle of the main shaft in the middle layer is circumferentially symmetrical with the coaxial eccentric circles on two sides in the axial direction by 180 degrees of the axis of the main shaft.