WO2009149616A1

WO2009149616A1 - A revolving cylinder compressor

Info

Publication number: WO2009149616A1
Application number: PCT/CN2009/000359
Authority: WO
Inventors: 陈君立; 倪桂樵
Original assignee: 台州市压缩机制造有限公司
Priority date: 2008-06-13
Filing date: 2009-04-02
Publication date: 2009-12-17
Also published as: CN201218174Y

Abstract

A revolving cylinder compressor, includes a revolving cylinder block (4) and working pistons (7), wherein two cylinder holes which are vertical to an axis of the revolving cylinder block (4) and vertical from each other are provided in the cylindrical revolving cylinder block (4), the working pistons (7) are correspondingly provided in the two cylinder holes, and connected in match with eccentric journals on an eccentric shaft (1) by piston holes bearings (5). The revolving cylinder compressor reduces manufacturing cost without an intake valve and an exhaust valve.

Description

Rotary cylinder compressor

The utility model belongs to the technical field of a positive displacement compressor, and particularly relates to a rotary cylinder compressor which is provided with two working cylinders and realizes double cylinder double action.

Background technique

In the existing mechanical motion mechanism, there are various kinds of motion and transmission mechanisms such as a crank linkage mechanism, a gear transmission mechanism, a rack and pinion mechanism, a cam mechanism, a rocker slider mechanism, an eccentric shaft mechanism, a belt transmission mechanism, and the like. Each feature and use has different transmission efficiency and production cost. For example, it is used on engines, on volumetric compressors, and on high-pressure piston pumps. Crank-link mechanisms are the most common type of mechanism. The most outstanding feature of the crank-and-rod mechanism products is that the machining precision of the components is relatively high, the processing cost is high, the friction pairs of the mechanism are relatively high, the transmission efficiency is relatively low, and the product size and weight are relatively large. . For example, a reciprocating piston gas compressor driven by a crank-and-rod mechanism is the most commonly used compressor product, but in this type of volumetric gas compressor product, an intake valve and an exhaust valve are provided. There are valve chamber "clearance volumes" of different sizes in the compression chamber of the cylinder. These harmful "clearance volumes" will affect the volumetric efficiency of the gas compressor and reduce the actual displacement of the cylinder. Moreover, the suction and exhaust valves in each cylinder are the main sources of noise in the operation of gas compressors. The mass imbalance factor of the crankshaft and the connecting rod moving parts is the source of vibration in the operation of the compressor product.

Utility model content

In view of the problems existing in the prior art, the object of the present invention is to provide a technical solution for a rotary cylinder compressor, which combines two types of motions, a rotary motion and a reciprocating motion, in the same motion mechanism. There is no need to install suction and exhaust valves, which improves work efficiency and reduces production costs.

The rotary cylinder compressor includes a rotary cylinder block and a working piston, wherein the cylindrical rotary cylinder block is axially disposed with two cylinder bores perpendicular to the axis of the rotary cylinder block and 90° apart from each other, two A working piston is correspondingly arranged in the cylinder bore, and the working piston is coupled with the eccentric journal on the eccentric shaft through the piston bore bearing.

The rotary cylinder compressor is characterized in that the left cylinder head and the right cylinder head are arranged at both ends of the rotary cylinder block, and the left cylinder head and the right cylinder head are fixedly connected with the cylinder casing provided outside the rotary cylinder, and the rotary cylinder block is rotated. The cylinder block bearing is in rotational engagement with the cylinder housing or the left cylinder head and the right cylinder head.

The rotary cylinder compressor is characterized in that the eccentric shaft and the rotary cylinder block rotate around respective rotation centers, and the rotation direction is the same, and the rotation speed ratio is 2:1.

The rotary cylinder compressor is characterized in that the working piston is slid in the rotary cylinder body through an eccentric journal on the eccentric shaft, and the movable stroke is four times the eccentric shaft eccentricity.

The rotary cylinder compressor is characterized in that a Gly sealing ring is disposed on an outer cylindrical surface or both end faces of the rotary cylinder block.

The rotary cylinder compressor is characterized in that the piston bore bearing adopts a double bearing sleeve structure.

The utility model drives the piston through the eccentric shaft on the eccentric shaft, so that the cylinder body performs the rotary motion, and the piston slides in the cylinder bore of the cylinder body to reciprocate, opposite to the fixed cylinder housing, the two ends of the piston There is a working process of inhaling, compressing and venting, and such a double-acting working process improves work efficiency. The suction port and the exhaust port are opened on the cylinder housing, and the suction and exhaust processes are realized by a specific phase switching relationship between the outer cylindrical surface of the cylinder body and the inner hole surface of the casing, thereby eliminating the need to provide suction and exhaust valves, thereby reducing The production cost is also reduced, and the valve impact noise generated during the work process is also reduced. The symmetry of the motion mechanism ensures the balance of the product during operation, no need to set the unbalanced weights, and reduce the noise. It also reduces the weight of the product.

DRAWINGS

Figure 1 is a schematic cross-sectional view of the utility model;

Figure 2 is a schematic diagram of the gas distribution phase of the utility model;

Figure 3 is an enlarged schematic view of the end face sealing structure of the rotary cylinder;

Figure 4 is a schematic enlarged view of the structure of the piston bore bearing;

Figure 5 - Figure 8 is a schematic diagram of the working process of the present invention.

detailed description

The cylindrical rotary cylinder block 4 is axially disposed with two cylinder bores perpendicular to the axis of the rotary cylinder block 4 and 90° apart from each other. The working piston 7 is disposed in the cylinder bore, and the working piston 7 passes through the piston bore bearing 5 and is eccentric. The eccentric journal on the shaft 1 is coupled and the piston bore bearing 5 adopts a double bearing sleeve structure to improve the adaptability of the working piston 7 to slide in the cylinder bore of the rotating cylinder block 4, thereby improving the motion precision and reducing wear. The left cylinder head 9 and the right cylinder head 3 are disposed at both ends of the rotary cylinder block 4. The left cylinder head 9 and the right cylinder head 3 are fixedly connected with the cylinder housing 6 provided outside the rotary cylinder block 4, and the rotary cylinder block 4 is rotated by the cylinder block. The bearing 8 is in rotational engagement with the cylinder housing 6 or the left cylinder head 9 and the right cylinder head 3. A gleaming sealing ring 13 is arranged on the outer cylindrical surface or both end faces of the rotary cylinder block 4, and a surface contact seal is used to prevent the high-pressure gas on the top surface of the rotating cylinder block 4 from leaking into the transmission shaft cavity, thereby ensuring a high pressure. Reduced efficiency, good sealing effect and low leakage loss.

In operation, the eccentric shaft 1 is supported and rotated by the eccentric shaft bearing 2, thereby driving the working piston 7 to rotate the rotating cylinder block 4 in the same direction. Since the eccentric shaft 1, the rotating cylinder block 4 and the working piston 7 are not on the same center line, There is a fixed eccentricity e between them, so that the working piston slid in the cylinder bore of the rotating cylinder block 4 under the eccentric shaft of the eccentric shaft 1 to reciprocate, and its reciprocating motion The maximum stroke is 4e, and the rotational speed ratio η1 _: π2 of the eccentric shaft 1 and the rotary cylinder block 4 about the respective rotation centers is 2:1. There is a deflection angle Φ between the center line of the eccentric shaft 1, the rotating cylinder block 4 and the working piston 7 and the center line of the cylinder housing 6. This deflection angle Φ is called the valve phase angle, and its deflection direction (Right or leftward) It is related to the direction of rotation of the main shaft and has a specific relationship with the position of the intake and exhaust ports on the casing. Therefore, after the deflection angle Φ is determined, the positions of the intake port 10, the suction chamber 11, and the exhaust port 12 on the cylinder housing 6 can be determined. As shown in Fig. 2, for each cylinder working chamber, during one revolution: Ρ is the suction process angle, ε is the compression process angle, and Θ is the exhaust process angle.

The working process principle of the utility model is shown in Fig. 5-8. Two working chambers Β and Β are formed at each end of the piston of each cylinder, as shown in FIG. The center point of the rotary cylinder block 4 is 0, the center point of the eccentric shaft 1 is 0 ₂ , and the center point of the working piston 7 is 0 ₃ . The working piston 7 shown in Fig. 6 is at the bottom dead center (or upper and lower dead center) position, the blow cylinder is the suction end point, and the B cylinder is the exhaust end point. At this time, the three cores of 0 ₂ and 0 ₃ The angle Φ between the line and the mid-perpendicular line of the casing 6 is the piston stop angle, that is, the valve phase angle Φ, which determines the phase angle of the intake and exhaust ports on the casing 6. As shown in Fig. 7, the piston is in the center position of the cylinder, the working chamber is in the inhaling process, and the working chamber is in the exhausting process. At this time, the center 0 _{3 of the} piston and the center 0 of the cylinder are in an overlapping position. As shown in Figure 5, the A-cylinder intake will end and the B-cylinder exhaust will end. Figure 8 is similar to Figure 6, except that the A and B cylinders are swapped for one phase, that is, the rotating cylinder block 4 is rotated by 180°, at which point the eccentric shaft 1 has been rotated 360°.

Therefore, for the utility model, a double-cylinder double-acting structure is adopted, two cylinder bores are arranged at a phase angle of 90°, the eccentric shaft 1 is rotated by 720°, and the rotary cylinder block 4 is rotated by 360°, and the two cylinder bores are externally outputted. 4 times compressed air, the structure of the host has good running balance performance, the outward supply frequency is very high, and the supply pressure fluctuation is small.

Claims

Claim

1. A rotary cylinder compressor comprising a rotary cylinder block (4) and a working piston (7), characterized in that two cylindrical cylinders (4) are disposed perpendicular to the axis of the rotary cylinder block (4) and mutually The cylinder bore of 90°, the working piston (7) is correspondingly arranged in the two cylinder bores, and the working piston (7) is connected with the eccentric journal on the eccentric shaft (1) through the piston bore bearing (5).

The rotary cylinder compressor according to claim 1, characterized in that the rotary cylinder block (4) is provided with a left cylinder head (9), a right cylinder head (3), a left cylinder head (9), and a right end. The cylinder head (3) is fixedly connected to the cylinder housing (6) provided outside the rotary cylinder block (4), and the rotary cylinder block (4) is rotated by the cylinder block bearing (8) with the cylinder housing (6) or the left cylinder head ( 9), the right cylinder head (3) is rotated.

A rotary cylinder compressor according to claim 1, wherein the eccentric shaft (1) and the rotary cylinder (4) are rotated about respective rotation centers in the same direction of rotation, and the rotation ratio is 2:1.

4. A rotary cylinder compressor according to claim 1, wherein the working piston (7) is slid in the rotary cylinder block (4) by an eccentric journal on the eccentric shaft (1), and the movable stroke is an eccentric shaft ( 1) 4 times the eccentricity.

A rotary cylinder compressor according to claim 1, wherein a gly sealing ring (13) is provided on an outer cylindrical surface or both end faces of the rotary cylinder block (4).

A rotary cylinder compressor according to claim 1, wherein the piston bore bearing (5) has a double bearing sleeve structure.