CN117090763A - Rotary plunger compression mechanism, hydraulic pump thereof and air compressor - Google Patents

Abstract

The invention belongs to the technical field of high-pressure plunger pumps. The stator is a circular cylinder barrel, and the rotor is a rotary cylinder cavity and a rotary plunger. The rotary plunger reciprocates in the rotary radial cylinder cavity to compress and expand the front and rear chambers of the plunger. The two ends of the combined crankshaft are supported in the eccentric holes of the front end cover and the rear end cover, the crankshaft diameter drives the plunger to revolve, and meanwhile, the main shaft diameter gear reduces half speed to drive the cylinder cavity and the plunger to rotate. The plunger completes one compression stroke every revolution, and the plunger and the cylinder cavity complete one compression direction conversion every half revolution. The revolution of the plunger and the rotation of the plunger and the cylinder cavity realize the unidirectional continuous compression of the plunger in the cylinder cavity. The advantages are that: 1. the chambers at the two ends of the plunger are simultaneously working, so that the efficiency is improved by times. 2. The plunger unidirectional continuous pressure discharge device has no intermittent pressure and stable output. 3. The plunger compression stroke is long, the compression ratio is large, and the output pressure is large. 4. The volume rate of the cylinder cavity is high, and the displacement ratio is large. 5. All are face seals, sealing well and wear resistant.

Description

Rotary plunger compression mechanism, hydraulic pump thereof and air compressor

Technical Field

The invention relates to a volumetric rotary plunger compression mechanism, and belongs to the technical field of high-pressure plunger pumps.

Background

The existing hydraulic pump mainly has three types: 1. the gear pump can continuously output large flow, but the output pressure is low (5-15 mpa). The pump is used as a liquid pressure pump, and 2, the vane pump can continuously output medium flow and medium pressure (15-25 mpa). For small hydraulic machines. 3. The plunger pump has small output flow, but can output high pressure (25-40 mpa) and is used for a crane excavator.

The output pressure of the existing swash plate plunger pump is highest and is only 40mpa, and the structural defects limit the performance to be improved again: 1. the included angle of the inclined disc is 15-20 degrees, and the included angle of the inclined disc cannot be too large, so that the enlargement of the compression stroke is limited, and the output pressure is difficult to rise again. 2. The force of the swash plate depressing the plunger is only the axial component of the swash plate rotation, only accounts for about 70% of the input power, and has inclined plane and friction resistance of the plunger top to consume work. 3. The conversion between the oil inlet and the oil outlet is realized by friction rotation of the valve plate under the back pressure seal, the friction resistance consumes about 30 percent of work, and the total mechanical energy of the prime motor is only about 50 percent converted into hydraulic energy, so that the efficiency is low. 4. The oil suction and oil discharge need the plunger to go and go once each, the plunger only has one end cavity to work, and the intermittent oil discharge flow is small. Oil pressure fluctuation is reduced by alternate oil discharge from multiple cavities.

In summary, the output pressure of the existing swash plate type plunger pump is 40mpr at the highest, and the flow rate is small and the efficiency is low. With the development of heavy machinery, high-efficiency hydraulic pumps with higher output pressures (e.g., 100 mpa) and larger flows are required.

The performance of the existing air compressor is briefly described: the existing air compressors for pneumatic machines mainly have two types: 1. the reciprocating piston type air compressor can generate high air pressure and intermittently output, and the reciprocating inertial force is difficult to balance, so that the rotating speed cannot be too high, and the output flow is small. 2. The screw air compressor has good dynamic balance, high rotating speed and large output flow. But the sealing performance is poor, and only medium pressure can be output.

The method comprises the following steps: the reciprocating piston type air compressor can output high-pressure gas, but cannot rotate at a high speed, and the output flow is small. The screw air compressor can have high rotating speed and large output flow, but has poor sealing performance and can only output medium pressure. What is needed is a high-efficiency air compressor that can output both high pressure and large flow rate for large pneumatic devices.

The invention aims to provide a compression mechanism which can output ultrahigh pressure and large flow and is efficient and energy-saving, and the product of the compression mechanism comprises a hydraulic pump and an air compressor, and is used for a hydraulic system and quick pneumatic equipment of a large-scale engineering machine.

Disclosure of Invention

The invention creates a rotary plunger compression mechanism: in the stator housing, a radial cylinder chamber 18 is provided on the rotary cylinder 5, and the plunger 6 in the cylinder chamber 18 reciprocates relative to the cylinder chamber 18 during revolution along the crank shaft diameter 7, so that the chambers at both ends of the plunger 6 perform compression and expansion working strokes, respectively. The plunger 6 completes one movement stroke with each revolution of the crank shaft diameter 7, namely, completes the movement stroke of the plunger 6 from the end A to the end B of the cylinder cavity 18, the chamber B at the front end of the plunger 6 in the cylinder cavity 18 is compressed and discharged in the following revolution, and the chamber A at the rear end of the plunger 6 is expanded and sucked in the following revolution. The plunger 6 completes the transposition of the two ends of the cylinder cavity and the plunger along with each half rotation of the cylinder cavity 18, so that when the plunger 6 makes the next revolution along with the crank shaft diameter 7, the plunger 6 can move back from the end B to the end A of the cylinder cavity 18. The plunger 6 rotates with the crank shaft diameter 7 for one circle, and the plunger 6 rotates with the cylinder cavity 18 for half a circle of compound movement, so that the unidirectional compression stroke of the plunger 6 from one end to the other end of the cylinder cavity 18 can be realized by rotating each circle of the crank shaft diameter 7. Whereby the chambers at both ends of the plunger 6 are successively sucked in by turns at the fixed point suction inlet 10 and successively discharged by turns at the fixed point discharge outlet 11.

First innovation point: ultra-long compression stroke: the plunger 6 rotates for one circle under the drive of the crank shaft diameter 7, the plunger 6 rotates for half a circle on the crank shaft diameter 7, and the superposition of two rotating speeds realizes the lengthening stroke of the plunger 6, namely the compression movement of the plunger 6 from one end to the other end of the cylinder cavity 18 in a straight line in the cylinder cavity 18. The principle is as follows: the upper half of each revolution of the plunger 6 is the 'go' stroke and the lower half is the 'return' stroke. The lower half turn is also changed to the 'forward' stroke, and the plunger 6 needs to rotate for one turn while rotating for another half turn, that is, the positions of the cylinder chamber 18 and the two ends of the plunger 6 are rotated by an angle of 180 ° in the middle, so that the 'forward' stroke of the lower half turn of the plunger 6 is changed to the 'forward' stroke, and the 'forward' + 'forward' extension compression stroke is changed.

And a second innovation point: the chambers at two ends of the plunger work simultaneously: the plunger 6 divides the cylinder chamber into two chambers within the radial cylinder chamber 18. The plunger 6 is driven by the crankshaft diameter 7 in the central hole to rotate for one circle, and the plunger 6 is driven by the cylinder cavity 18 where the plunger 6 is positioned to rotate around the crankshaft diameter for half a circle. Each revolution of the plunger 6 overlaps half-turn rotation of the plunger 6 to form an lengthening movement stroke of the plunger 6 in the cylinder cavity 18, so that the front cavity and the rear cavity of the plunger 6 work simultaneously: the front chamber is in the compression stroke and the rear chamber is in the suction stroke. The conversion between the compression stroke and the suction stroke of the two chambers is realized by half a turn of each of the cylinder chamber 18 and the plunger 6.

And (3) an innovation bright point III: wheel flow continuous type pressure row: the first revolution of the plunger 6 forms the compression stroke of the plunger 6 from the end A to the end B of the cylinder cavity 18, meanwhile, the cylinder cavity 18 rotates about the center of the circle for half a circle, the cylinder cavity 18 drives the plunger 6 to rotate about the crank shaft diameter 7 for half a circle, and the chambers at the two ends of the plunger 6 are converted by 180 degrees, namely, the chamber at the rear end of the plunger 6 is converted into the chamber at the front end. Whereby the second revolution of the plunger 6 forms a compression stroke of the plunger 6 from the B end to the a end of the cylinder chamber 18. The compression stroke of the two chambers is compressed in the same direction in turn. Whereby a continuous compression discharge from the fixed-point discharge port 11 is formed.

The practicability of the compression mechanism of the invention is that: the feasibility and the practicability of the compression mechanism are proved by a prototype experiment, and the compression mechanism has the advantages that: 1. in the rotary cylinder cavity, the co-rotary plunger makes reciprocating compression motion relative to the cylinder cavity, the cylinder cavity at one end of the plunger is sucked in during the pressure discharge, the cylinder cavities at two ends of the plunger work simultaneously, the efficiency is doubled, and the energy conservation and the high efficiency are realized. 2. The cylinder cavity and the plunger complete the conversion position in the rotation half circle, so that each circle of stroke of the plunger is a unidirectional compression stroke. The continuous pressure discharge is formed, the liquid discharge is not intermittent, and the output pressure is stable. 3. The length of the compression stroke is the 'forward' + 'forward' stroke of one circle of crankshaft diameter, and is twice the reciprocating stroke of the piston of the existing crankshaft connecting rod. The compression stroke is long, the output pressure is high for liquid, the output flow is high, the compression ratio is high for gas, and the output air pressure is high. 4. The volume rate of the cylinder cavity of the structure is large, and the output flow is large.

The structure of the invention is briefly described as follows: see fig. 1 and 2. Front and rear end caps 3 are fixed to both ends of the combined outer tube 20, and serve as stator portions. The main shaft diameters 8 at both ends of the combined crankshaft 19 are supported on eccentric holes of the front and rear end caps 3. The two ends of the cylinder 5 are supported on the inner bosses of the front and rear cylinder heads 3. The combined crankshaft 19 is provided with a plunger 6 in a sleeved mode on the crankshaft diameter 7, the plunger 6 is arranged in a radial cylinder cavity 18 of the cylinder 5, and the cylinder 5 is driven by a main shaft diameter gear 8 of the combined crankshaft. Is a rotating part.

Stator component: the combined outer cylinder 20 is formed by embedding a sleeve 2 in an outer shell 1. The outer shell 1 is provided with a suction inlet 10 and a discharge outlet 11 respectively at two sides of the middle section of the cylinder. The sleeve 2 has two inner inlet holes 12, 13 and two inner outlet holes 15, 16 on two sides of the middle section of the cylinder. Between the outer shell 1 and the sleeve 2 of the combined outer barrel 20, one side is provided with a suction inner channel 14 which is communicated with two inner inlet holes to the suction inlet 10, and the other side is also provided with a discharge inner channel 17 which is communicated with two inner outlet holes to the discharge outlet 11. Two positioning grooves and uniformly distributed screw holes are respectively arranged on the circumferences of two ends of the outer shell 1 of the combined outer barrel 20 and are used for fixing the front end cover 3 and the rear end cover 3. The front and rear end caps 3 have the same structure, and two stages of bosses are arranged on the inner plane of the front and rear end caps, and the outer bosses are used for positioning and fixing the sleeve 2 of the combined outer cylinder 20. The inner boss is provided with a sliding bearing sleeve for supporting two ports of the rotary cylinder 5. The outer plane of the front end cover 3 and the outer plane of the rear end cover 3 are provided with concave tables, and the concave table cavities are counterweight chambers. The boss of the front and rear end caps 3 has a circular hole with an eccentric e, and a sliding shaft sleeve is installed in the hole for supporting the main shaft diameter 8 at two ends of the combined crankshaft 19.

And a rotating part: the combined crankshaft 19 is formed by respectively inserting flat shafts of the main shaft diameter 8 at two ends of a flat hole of the crankshaft diameter 7. The crank shaft diameter 7 is a cylinder, and two end surfaces of the crank shaft diameter are provided with through flat holes with the eccentric value of e. The main shaft diameter (gear shaft) 8 is provided with a gear at the middle section, one end of the gear is a flat shaft, and the other end of the gear is a cylindrical shaft, namely the main shaft diameter. The main shaft diameters 8 at the two ends of the combined crankshaft 19 are supported in eccentric holes of the front end cover 3 and the rear end cover 3, and the main shaft diameters 8 extending out of the holes are provided with balancing weights. The main shaft at one end of the motor is longer in diameter and provided with a spline, and is connected with the motor shaft. The plunger 6 is sleeved on the crank shaft diameter 7 of the group and the crank shaft 19, the plunger 6 is a square cuboid with four round corners, the top surfaces of two ends of the plunger are cylindrical surfaces, the side surfaces of the plunger are provided with central holes, and sliding sleeve bearings are sleeved on the crank shaft diameter 7. The plunger 6 is arranged in a radial cylinder cavity 18, and the radial cylinder cavity 18 is a rectangular four-corner long hole which is penetrated in the radial direction in the middle of the cylinder body of the cylinder barrel 5. Concave platforms are arranged at two ends of the cylinder barrel 5 and are supported on inner bosses of the front end cover 3 and the rear end cover 3.

Drawings

Reference numerals in the drawings: 1-shell, 2-sleeve, 3-front and rear end covers, 4-cover plate, 5-cylinder barrel, 6-plunger, 7-crank shaft diameter, 8-crank shaft diameter (tooth shaft), 9-balancing weight, 10-suction inlet, 11-discharge outlet, 12-inner inlet hole, 13-inner inlet hole, 14-inner inlet channel, 15-inner outlet hole, 16-inner outlet hole, 17-inner outlet channel, 18-cylinder cavity, 19-combined crank shaft and 20-combined outer barrel.

Fig. 1 is a longitudinal cross-sectional view of a rotary plunger compression mechanism.

Fig. 2 is a transverse cross-sectional view of a rotary plunger compression mechanism (fig. 1).

Fig. 3 is a transverse cross-sectional view of a rotary plunger hydraulic pump.

Fig. 4 is a transverse cross-sectional view of a rotary plunger air compressor.

Fig. 5 is a schematic diagram of the operation of the rotary plunger hydraulic pump.

Fig. 6 is a schematic diagram of the working process of the rotary plunger air compressor.

Fig. 7 is a photograph of a rotor assembly of a rotary plunger compression mechanism.

Fig. 8 is a photograph of a cylinder part of a rotary plunger compression mechanism.

Fig. 9 is a photograph of a plunger piece of a rotary plunger compression mechanism.

Detailed Description

The transmission mode is as follows: when the motor drives the main shaft diameter 8 of the combined crankshaft 19 to rotate, the crankshaft diameter 7 of the combined crankshaft 19 carries the plunger 6 to revolve, and meanwhile, the gear of the main shaft diameter (gear shaft) 8 of the combined crankshaft 19 is reduced to drive the internal gear on the cylinder 5, so that the cylinder 5 rotates at half speed, and the plunger 6 in the cylinder cavity 18 on the cylinder 5 also rotates at half speed. The plunger 6 is reciprocally moved relative to the cylinder cavity during the rotation of the plunger 6 by overlapping the rotation half-turn of the plunger 6 every revolution of the plunger 6, so that the chambers at both ends of the plunger 6 alternately complete the suction and discharge working strokes.

The specific application is as follows: the rotary plunger compression mechanism is used as the optimal hydraulic pump and also used as the gas compressor, the rotor structures of the rotary plunger compression mechanism and the gas compressor are the same, and the working processes are the same. Except for the outlet. As described in detail below.

The working process of the rotary plunger hydraulic pump comprises the following steps: referring to fig. 3 and 5, the sleeve 2 has two inner inlets on one side and two inner outlets on the other side. The liquid cannot be compressed, but can be pressurized and transmitted. The hydraulic pump is characterized by being capable of being discharged when being pressed. The liquid discharge starts from the start of the compression. The magnitude of the output pressure is determined by the magnitude of the compression stroke and the rate at which compression is performed.

Fig. 5 (1) shows that the end a of the plunger 6 is at the top dead center, the volume of the end a is at the minimum, the volume of the end B is at the maximum, and the crank diameter 7 is at a position directly above the center of the circle at the top dead center when the cylinder chamber is at the vertical position.

Fig. 5 (1) to (2) to (3) to (4) show that when the cylinder cavity and the plunger 6 rotate clockwise by 45 degrees, 90 degrees and 135 degrees in turn, the crank shaft diameter 7 rotates by 90 degrees, 180 degrees and 270 degrees in turn at double speed, and the plunger 6 is driven to move towards the end B of the cylinder cavity, so that the pressure drainage is continuously carried out on the end B cavity, and the liquid suction is continuously carried out on the end A cavity.

From fig. 5 (4) to (1), when the cylinder cavity and the plunger 6 rotate through an angle of 180 °, the crank shaft diameter 7 rotates through an angle of 360 ° at a double speed, and the plunger 6 is driven to reach the end point of the cylinder cavity B. The pattern at this time returns to the shape of fig. 5 (1). In contrast, the plunger 6 has its end B to top dead center, its end B to drain end, and its end A to maximum volume.

The working process of the rotary plunger air compressor comprises the following steps: see fig. 4 and 6. One side of the sleeve 2 is provided with two inner inlet holes, and the other side is provided with only one inner outlet hole which is directly communicated with the discharge outlet. The gas can be compressed and the magnitude of the output gas pressure is determined by the compression ratio. The air pump is characterized in that the air is exhausted when the air is compressed to a certain pressure. Compression begins after one end cylinder chamber is full of air, and no air is discharged until the compression end point is near.

Fig. 6 (1) shows the cylinder chamber in the vertical position with the a end of the plunger 6 at top dead center, the a end chamber volume at minimum, and the B end chamber volume at maximum. The crank diameter 7 is positioned right above the center of the circle at the top dead center.

Fig. 6 (1) to (2) to (3) show that the cylinder chamber and the plunger 6 are rotated by an angle of 45 ° and an angle of 90 ° and the crank diameter 7 is rotated by an angle of 90 ° and an angle of 180 ° at double speed. At this time, the crank shaft diameter 7 is rotated to the position right below the center of the circle, and the plunger 6 is driven to move towards the end B. The A end cavity continuously sucks air, and the B end cavity continuously compresses air.

Fig. 6 (3) to (4) show that when the cylinder cavity and the plunger 6 rotate by 135 degrees, the crank shaft diameter 7 rotates by 270 degrees at double speed, and the plunger 6 is driven to move towards the end B. The B-side chamber begins to vent. The a-side chamber continues to inhale.

From fig. 6 (4) to (1), when the cylinder cavity and the plunger 6 are rotated by 180 degrees, the crank diameter 7 is rotated by 360 degrees at a double speed, the plunger 6 is driven to reach the end point of the end B, and the graph returns to the shape of fig. 6 (1). Except that the end B of the plunger 6 is at top dead center, the end B chamber is at the exhaust terminus, and the end a chamber is at the maximum volume.

The product has the advantages that: the rotary plunger compression mechanism has the advantages of the hydraulic pump and the air compressor which are the application products of the rotary plunger compression mechanism: 1. compact structure, small volume, high power, high efficiency and energy saving. 2. The compression stroke is large, the compression ratio is large, and the output pressure is large. 3. The volume ratio is large, the rotating speed can be high, and the output flow is large. 4. The continuous pressure discharge is not intermittent, and the output pressure is not fluctuated. 5. The seal is a wide-area sliding seal, has good sealing performance, is wear-resistant and has long service life. 6. No complex curved surface, easy manufacture and low cost.

The specific application is as follows: the rotary plunger compression mechanism solves all the problems of the existing high-pressure plunger pump, and the output pressure and the output flow are improved by times. The invention is a new structure of continuous compression and discharge of rotary plunger in rotary cylinder cavity, which occupies the high-end field of plunger pump with excellent performance, and has two types: the hydraulic pump with superhigh pressure, superhigh flow rate, high efficiency, low power consumption and low cost may be used to replace available various kinds of high pressure pump for large engineering machinery and large weapon system, especially hydraulic system for airplane. The other is a high-pressure, high-flow, high-efficiency and energy-saving air compressor, which can replace the existing low-efficiency reciprocating, low-pressure screw type and poor-sealing rotor type air compressor. The device is used for large-scale rapid pneumatic machines, pneumatic ejection machines, pumps for vacuumizing and the like which need high-pressure air. In conclusion, the invention has great significance for the national technical progress.

Claims (9)

1. A rotary plunger compression mechanism, characterized by: it comprises the following steps: the combined outer cylinder (1, 2), front and rear end covers (3), a cylinder barrel (5), a plunger (6) and combined crankshafts (7, 8).

2. The combined outer cylinder (1, 2) according to claim 1 is characterized in that: the sleeve (2) is embedded in the outer shell (1). Two sides of the middle section of the outer shell (1) are respectively provided with: a suction inlet (10) and a discharge outlet (11). Two inner inlet holes (12, 13) and two inner outlet holes (15, 16) are respectively formed in two sides of the middle section of the sleeve (2), and two inner channels are respectively formed in two sides between the outer shell of the combined outer cylinder and the sleeve: 1. an inner suction passage (14) connecting the two inner inlets to the suction inlet; 2. an inner discharge passage (17) connects the two inner discharge holes to the discharge port.

3. Front and rear end caps (3) according to claim 1, which are structurally identical. The novel end cover is characterized in that two stages of bosses are arranged on the inner plane of the end cover, and a hole with the eccentric distance of e is arranged in the center of the boss plane. The outer plane of the front end cover (3) and the outer plane of the rear end cover (3) are provided with a concave table, and the inner cavity of the concave table is a counterweight chamber.

4. The cylinder (5) according to claim 1, characterized in that: the middle part of the cylinder barrel cylinder body is provided with a radial cylinder cavity hole with rectangular four corners. The cylinder barrel (5) is provided with concave tables at two ends of the cylinder body. The centers of the concave table planes at the two ends of the cylinder barrel (5) are respectively provided with the same internal gear hole.

5. Plunger (6) according to claim 1, characterized by a rectangular quadrangle cuboid with the end faces of the two ends being cylindrical surfaces. The two side surfaces of the plunger (6) are provided with a central hole, and copper bush sliding bearings are arranged in the central hole.

6. The combined crankshaft (7, 8) according to claim 1, characterized in that: is formed by respectively inserting flat shafts on two main shaft diameter tooth shafts (8) into eccentric flat holes on two end surfaces of a cylinder body of a crank shaft diameter (7). Namely, the middle section is a crank shaft diameter (7), and the two ends are main shaft diameters (8).

7. Crank diameter (7) according to claim 6, characterized by a cylinder with a through flat hole with an eccentricity e at its two end faces.

8. The main shaft radial tooth shaft (8) according to claim 6, characterized in that: one side of the gear is a flat shaft, and the other side of the gear is a cylindrical shaft, namely a main shaft diameter (8). The cylindrical shaft end of one of the spindle diameter gear shafts (8) is provided with a spline.

9. The rotary plunger compression mechanism of claim 1, comprising a hydraulic pump and an air compressor, characterized in that: the oil discharge channel of the hydraulic pump is formed by two inner outlet holes and is connected to the oil discharge port through the inner discharge channel. The exhaust channel of the air compressor has only one inner outlet hole which is directly communicated with the exhaust port.