CN216008795U - Parallel six-star piston compressor - Google Patents

Abstract

A parallel six-star piston compressor comprises a machine body, a cylinder, a rotary reciprocating motion conversion device and a driving device; the six rows of cylinders are uniformly arranged around the rotation center of the rotary reciprocating motion conversion device at intervals of 60 degrees, and the center lines of the six rows of cylinders are positioned on different planes and are perpendicular to and intersected with the rotation center axis; the rotary reciprocating motion conversion device comprises a single-throw crankshaft, six connecting rods connected with a crank pin of the single-throw crankshaft and six pistons connected with the six connecting rods, the six connecting rods are arranged on the crank pin in parallel, the six pistons reciprocate in six cylinders, the cylinders and the crankshaft of the rotary reciprocating motion conversion device are arranged on the machine body, and the crankshaft of the rotary reciprocating motion conversion device is connected with a driving shaft of the driving device. The utility model has the advantages of compact structural layout, energy saving, weight reduction, stable stress, small torque fluctuation, small airflow pulsation, small working vibration, low noise and good cooling effect of the whole machine.

Description

Parallel six-star piston compressor

Technical Field

The utility model relates to a piston compressor arranged in a parallel star manner, in particular to a six-cylinder full-oil-free lubrication piston compressor arranged in a parallel star manner.

Background

The oil-free lubrication piston type compressor loses the lubrication and cooling effects of lubricating oil due to the fact that the lubricating oil is not used, the heat load problem of the compressor is particularly prominent, in practical application, the wear-resistant material of the oil-free piston is limited by a pv value, p is the bearing specific pressure of the material, v is the linear velocity reached by the material, and meanwhile the material can be softened at a certain temperature. Therefore, under the condition of meeting the gas output requirement of the same displacement and pressure, if a large cylinder diameter is adopted, the rotating speed of the machine must be reduced, meanwhile, the increase of the cylinder diameter is also limited by the heat dissipation of the cylinder, and if a high rotating speed is adopted, the cylinder diameter of the compressor must be reduced, and under the same displacement pressure, the number of the cylinders of the compressor must be increased.

The structure of the totally oil-free lubricating compressor in the current market is mostly V, W type products, the tangential force load of the product with the structure is uneven, the stress of the whole machine is unstable, the vibration during working is large, and the load change of the power device of the air compressor is large, so that the service life of the compressor is shortened. In addition, the existing air compressor has larger working noise. Meanwhile, V-shaped and W-shaped cylinders are adopted, and only two-stage or three-stage compression can be adopted due to the small number of cylinders, so that high compression pressure is difficult to realize.

In the field of new energy vehicles, particularly the field of new energy commercial vehicles, due to the maintenance-free advantage of an oil-free compressor, the application of the oil-free compressor is rapidly popularized, the new energy commercial vehicle increases the gas consumption requirement beyond brake braking, the discharge capacity and the pressure of the compressor are also promoted year by year, and the commonly adopted motor two-end 2V-shaped four-cylinder structure can not meet the use requirement of the current large gas amount. Due to the limitation of the automobile field on the weight and the volume of automobile parts, the oil-free piston type compressor generally adopts a mode of small cylinder diameter, multiple cylinders and high rotation speed.

Patent CN 104895757A discloses a six jar oil-free piston air compressor, has adopted two W structures, realizes that the high pressure does not have the oil, and although first order inertia force is balanced, inertia force and moment unbalance more than the second order, the bent axle divide into the triplex simultaneously, and the structure is complicated, in order to guarantee the installation of bearing, and the bent axle is eccentric little.

In patent CN 209414067U, a six-cylinder oil-free piston air compressor is disclosed, in which the two ends of the motor are in 3-cylinder structure, and an eccentric sleeve shaft is adopted, so that the single-end crankshaft is divided into at least 4 parts, and the structure is complex. Although the first order inertial forces may be balanced, reducing vibration to some extent, the unbalanced moment is large.

In patent CN 210738753U, a six-star high-pressure compressor is disclosed, which adopts a conventional main-auxiliary connection structure, but there are the problems of inconsistent motion laws, inconsistent stroke and poor balance of inertia force of the main connecting rod piston and the auxiliary connecting rod piston, and in the oil-free application, the bearing for sealing oil grease is adopted, which will result in the diameter of the connecting rod disk increasing sharply, and the problem of imbalance will be more prominent.

Disclosure of Invention

The technical problem that this application embodiment will solve provides a six star piston compressors side by side, can realize gaseous full oil-free compression, simple structure, and the overall arrangement is compact, and energy-conservation subtracts heavy, and the atress is stable, and the moment of torsion is undulant little, and airflow pulsation is little, and the work vibration is little, and the noise is low, and the complete machine cooling effect is good. In a limited space, a large discharge amount or a high discharge pressure is achieved.

The application provides a six star piston compressors side by side, include, the organism, the cylinder, rotatory reciprocating motion conversion equipment, drive arrangement, its characterized in that:

the rotary reciprocating motion conversion device comprises a single-throw crankshaft, six pistons and six connecting rods for connecting the single-throw crankshaft and the six pistons, wherein the six pistons are uniformly arranged around the rotating center of the single-throw crankshaft at an interval of 60 degrees, the reciprocating motion center lines of the six pistons are positioned on different planes, one ends of the six connecting rods are arranged on crank pins of the single-throw crankshaft in parallel, and the other ends of the six connecting rods are respectively connected to the six pistons; the six rows of cylinders are uniformly arranged around the rotating center of the rotating reciprocating motion conversion device at intervals of 60 degrees and are in one-to-one correspondence with the six pistons, and the center lines of the six rows of cylinders are positioned on different planes and are perpendicular to and intersected with the rotating center axis; wherein six pistons of the rotary-to-reciprocating motion conversion device reciprocate in the six cylinders; the cylinder and the single-throw crankshaft of the rotary reciprocating motion conversion device are arranged on the machine body, and the single-throw crankshaft of the rotary reciprocating motion conversion device is connected with the driving shaft of the driving device.

Optionally, the parallel six-star piston compressor is characterized in that balancing weights are respectively arranged at two ends of the single throw crankshaft.

Optionally, the parallel six-star piston compressor is characterized in that the single-throw crankshaft is divided into a crank pin and a crank, and the crank pin is arranged in a crank pin hole of the rear crank through a crank pin.

Optionally, the parallel six-star piston compressor is characterized in that a support shaft diameter is arranged in the middle of the single throw crankshaft.

Optionally, the parallel six-star piston compressor is characterized in that bearings of sealing grease are adopted between the connecting rod and the crank pin and between the piston and the piston pin.

Optionally, the parallel six-star piston compressor is characterized in that at least a part of the outer surface of the piston, which is in contact with the inner wall of the cylinder, is coated with a self-lubricating wear-resistant layer.

Optionally, the parallel six-star piston compressor is characterized in that the surface of the inner wall of the cylinder is subjected to ceramic treatment.

Optionally, the parallel six-star piston compressor is characterized in that: and mounting bearing holes and driving device connecting holes are formed in the front end surface and the rear end surface of the machine body, and holes for mounting the air cylinders are formed in six side surfaces.

Optionally, the parallel six-star piston compressor is characterized in that the machine body is divided into two parts along the center of the rotary reciprocating motion conversion device, and each part is provided with a hole for mounting the cylinder and a bearing hole.

Optionally, the parallel six-star piston compressor is characterized in that the compressor is multi-stage compression, part or all of the pistons are stepped pistons, and the mass of each piston assembly is approximately equal.

Compared with the prior art, the utility model has the following advantages: the parallel six-star piston compressor of the embodiment of the application adopts a rotary reciprocating motion conversion device with the following structure: the six pistons are arranged on the crank pin in the following mode: the six pistons are uniformly arranged around the rotation center of the single-throw crankshaft at intervals of 60 degrees, the reciprocating motion center lines of the six pistons are positioned on different planes and are connected with the single-throw crankshaft through six connecting rods, one ends of the six connecting rods are arranged on crank pins of the single-throw crankshaft in parallel, and the other ends of the six connecting rods are respectively connected to piston pins of the six pistons; the three groups of pistons are arranged in a 180-degree opposite mode in pairs, the arrangement mode enables the first-order reciprocating inertia force of the pistons to be converted into centrifugal force acting on the crank pins, the first-order reciprocating inertia moment is zero, and the second-order reciprocating inertia force and the reciprocating inertia force above the second-order reciprocating inertia moment are self-balanced. After the first-stage reciprocating inertia force is balanced on the crank by arranging a balance configuration, only the second-stage reciprocating inertia moment with extremely small residual quantity is not balanced. The structural balance performance of the arrangement mode is greatly enhanced, so that the whole machine adopting the structure has excellent balance performance; further, in the conventional V-structure piston compressor, the crankshaft rotates for one circle, the two working cylinders reach the maximum pressure at an interval of 90 degrees within the range of the first 90 degrees, the subsequent 270 degrees and no pressure wave peak appear, the W-structure piston compressor, the crankshaft rotates for one circle and the range of the first 120 degrees, the three working cylinders reach the maximum pressure and the subsequent 240 degrees and no pressure wave peak appears, so that the V, W type compressor has uneven tangential force load, unstable stress of the whole compressor and large vibration during working, meanwhile, the load change of a power device of the air compressor is large, the crankshaft of the compressor rotates for one circle, six pistons work at an interval of 60 degrees, and the working cylinders discharge gas successively to reach the maximum pressure, so that the tangential force load is uniform, the stress is stable, the vibration is small, the airflow pulsation is small, and meanwhile, the torque fluctuation is small; furthermore, compared with the existing piston compressor with a W structure, the piston compressor with the crankshaft rotating for one circle has the advantages that the displacement is doubled under the condition that the width of the compressor body is lengthened by three connecting rods, and the structure is compact; further, compared with the existing piston compressor with the W structure, the piston compressor can realize at least 6 stages of compression; furthermore, compared with a double-W type compressor, the full balance of inertia force is realized, the vibration is smaller, the crankshaft is simpler, the axial size is small, the structure of the whole compressor is more compact, and the six cylinders are positioned on the windward side, so that the cooling effect is good; furthermore, compared with the conventional star-shaped structure, the piston compressor has no dynamic difference of the main connecting rod and the auxiliary connecting rod (figure 6), and the dynamics of the six pistons and the six connecting rods are consistent, so that a better balance effect can be obtained.

Drawings

Fig. 1 is a schematic structural diagram of a rotary-to-reciprocating motion conversion device of a parallel six-star piston compressor according to a first embodiment of the present application.

Fig. 2 is a schematic structural diagram of a parallel six-star piston compressor according to a first embodiment of the present application.

Fig. 3 is a schematic structural diagram of a crankshaft of a parallel six-star piston compressor according to a first embodiment of the present application.

Fig. 4 is a schematic structural diagram of a housing of a parallel six-star piston compressor according to a first embodiment of the present application.

Fig. 5 is a schematic view of a multistage compression structure using stepped pistons of a parallel six-star piston compressor according to a second embodiment of the present invention.

FIG. 6 is a graph comparing the piston velocity and acceleration of the conventional star-shaped main and auxiliary connecting rod structure.

Wherein: 01-a machine body, 02- (1-6) cylinders, 03-a rotary reciprocating motion conversion device, 04-a driving motor and 05-a base; 01-a,01-b are split bodies, 01- (1-6) are cylinder mounting holes of the bodies, 01-7,01-8 are spindle bearing mounting holes, 01-9 are motor flange mounting holes, 1- (1-6) are pistons, 2- (1-6) are connecting rods, 3 is a single-throw crankshaft, 3-1 crank pin, 3-2 crank and 3-3 positioning pins.

Detailed Description

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is capable of implementation in many different ways than those herein set forth and of similar import by those skilled in the art without departing from the spirit of this application and is therefore not limited to the specific implementations disclosed below.

The six-star piston type compressor comprises a machine body, a cylinder, a rotary reciprocating motion conversion device and a driving device and is characterized in that the rotary reciprocating motion conversion device comprises a single-throw crankshaft, six pistons and six connecting rods for connecting the single-throw crankshaft and the six pistons, the six pistons are uniformly arranged around the rotating center of the single-throw crankshaft at an interval of 60 degrees, the reciprocating motion center lines of the six pistons are located on different planes and are connected with the single-throw crankshaft through the six connecting rods, one ends of the six connecting rods are arranged on a crank pin of the single-throw crankshaft in parallel, and the other ends of the six connecting rods are connected to the six pistons respectively. The rotary reciprocating motion conversion device is driven to move by the force acting on the single-throw crankshaft, so that the conversion from rotary motion to reciprocating motion is realized; the six rows of cylinders are uniformly arranged around the rotating center of the rotating reciprocating motion conversion device at intervals of 60 degrees and are in one-to-one correspondence with the six pistons, and the center lines of the six rows of cylinders are positioned on different planes and are perpendicular to and intersected with the rotating center axis; wherein six pistons of the rotary-to-reciprocating motion conversion device reciprocate in the six cylinders; the cylinder and the single-throw crankshaft of the rotary reciprocating motion conversion device are arranged on the machine body, and the single-throw crankshaft of the rotary reciprocating motion conversion device is connected with the driving shaft of the driving device. The driving device drives the piston of the reciprocating motion conversion device to reciprocate in the cylinder to suck and compress gas. The machine body is matched with the driving device and the rotary reciprocating motion conversion device, and the driving device can be a motor or an internal combustion engine. The output power is determined according to the displacement and the rotating speed of the piston compressor.

The parallel six-star piston compressor is described in detail below with reference to specific embodiments.

The first embodiment.

The present embodiment is a piston compressor with a parallel six-star structure (or a quasi-six-star structure). Different from the main and auxiliary connecting rod structure of the conventional star engine, the parallel connecting rod structure is adopted in the utility model, the rotary reciprocating motion conversion device of the parallel six-star piston compressor in the embodiment is shown in fig. 1, and the rotary reciprocating motion conversion device in the embodiment is described below.

The rotary reciprocating motion conversion device of the parallel six-star piston type compressor comprises a single-throw crankshaft 3, six pistons 1-6 and six connecting rods 2-1-2-6 for connecting the single-throw crankshaft 3 and the six pistons, wherein the connecting rods corresponding to the six pistons 1-1,1-2,1-3,1-4,1-5 and 1-6 are 2-1, 2-2, 2-3, 2-4, 2-5 and 2-6. The arrangement mode of the piston and the connecting rod on the crank pin of the single-throw crankshaft is as follows: the motion directions of two adjacent pistons are spaced by 60 degrees, wherein the motion directions of two pistons 1-3 and 1-6 at the outermost sides, two pistons 1-2 and 1-5 at the middlemost, and two pistons 1-1 and 1-4 are respectively arranged at an angle of 180 degrees; namely, the six piston motion directions are separated by a set distance along the axial direction (the axial direction of the crank pin), and every two pistons are arranged in an angle of 180 degrees. The arrangement mode enables the first-order reciprocating inertia force of the piston to be converted into centrifugal force acting on the crank pin, the first-order reciprocating inertia moment is zero, and the second-order reciprocating inertia force is self-balanced. After the primary reciprocating inertia force can be balanced on the crank by arranging the balance configuration 3-1-1, 3-2-1 shown in figure 3, only the secondary reciprocating inertia moment with extremely small residual amount is not balanced. The structural balance performance of the arrangement mode is greatly enhanced, so that the whole machine has excellent balance performance, and mechanical vibration and noise are obviously reduced. Further, compared with the conventional star-shaped structure, the arrangement has no dynamic difference of the main connecting rod and the auxiliary connecting rod (figure 6), thereby obtaining better balance effect.

Fig. 2 shows a schematic structural diagram of the parallel six-star piston compressor of the present embodiment, and in the present embodiment, the parallel six-star piston compressor of the present embodiment is mainly described in combination with the arrangement form thereof, and a driving device and accessories of the compressor are not described much, and related points can refer to the existing piston compressor.

Referring to fig. 2, the parallel six-star piston compressor of the present embodiment includes six compression cylinders 02-1,02-2, 02-3, 02-4, 02-5 and 02-6 respectively disposed in six mounting holes 01-1, 01-2, 01-3, 01-4, 01-5 and 01-6 of a machine body 01 shown in fig. 4, and uniformly arranged at intervals of 60 °, and a rotary-reciprocating motion conversion device 03 is disposed therein, and a driving device is disposed behind the six compression cylinders, wherein the driving device is a driving motor 04 in the present embodiment. The entire machine is set on the base 05. The single-throw crankshaft 3 of the embodiment is connected with a driving shaft of the driving device 04, the driving device 04 drives the single-throw crankshaft 3 to rotate, and the single-throw crankshaft 3 drives the six connecting rods 2-1, 2-2, 2-3, 2-4, 2-5 and 2-6 of the embodiment to drive the six pistons 1-1,1-2,1-3,1-4,1-5 and 1-6 of the embodiment to reciprocate in the six cylinders 02-1,02-2, 02-3, 02-4, 02-5 and 02-6 of the embodiment to complete gas suction and compression.

In this embodiment, the connecting rods 2-1, 2-2, 2-3, 2-4, 2-5 and 2-6 are connected with bearings using sealing grease between the crank pins, the pistons 1-1,1-2,1-3,1-4,1-5 and 1-6 and the piston pins.

In the embodiment, at least the part of the outer surface of the piston 1-1,1-2,1-3,1-4,1-5 and 1-6, which is in contact with the inner wall of the cylinder, is coated with a self-lubricating wear-resistant layer.

In this embodiment, the inner wall surfaces of the cylinders 02-1,02-2, 02-3, 02-4, 02-5, and 02-6 are subjected to ceramization treatment.

As shown in fig. 3, the single-throw crankshaft in this embodiment is a split structure, in which the crank 3-2 and the crank pin 3-1 are detachable structures, and are fixed together by fasteners such as bolts and positioning pins 3-3, and the balance arrangement 3-1-1, 3-2-1 is located at both ends of the crankshaft. The single-throw crankshaft can also adopt an integrated structure and is designed into a snake-shaped structure, and the balance weight at the shaft end needs to be configured independently. Under the condition of heavy load use, the single-throw crankshaft can increase the diameter of the middle main shaft as a middle support so as to enhance the rigidity of the crankshaft.

Fig. 1 shows a preferred axial arrangement of pistons, which can adjust the sequence of the pistons in the direction of the crankshaft while ensuring that six pistons are arranged at 60 ° intervals, the connecting rods are adjusted accordingly according to the pistons, and the corresponding bodies and cylinders of the compressor are also adjusted accordingly according to the arrangement of the pistons.

Fig. 4 shows a split type body structure, in this embodiment, mounting bearing holes 01-7 and 01-8 and flange connecting holes 01-9 of a driving device 04 are formed on the front and rear end faces of the body 01, and holes 01-1 to 01-6 for mounting the cylinder are formed on six side faces, the body 01 is divided into two parts 01-a and 01-b along the center of the rotary reciprocating motion converting device 03, and each part is provided with a hole for mounting the cylinder and a mounting bearing hole. The machine body 01 may also be divided into two parts along any diagonal line of the hexahedron passing through the center of the rotary reciprocating motion conversion device 03, or divided into two parts along the central axis of the rotary reciprocating motion conversion device 03 passing through the central connecting line of any two opposite cylinders, or divided into two parts in front and back along the central axis perpendicular to the rotary reciprocating motion conversion device 03, or divided in other forms, which is mainly convenient for the installation of the rotary reciprocating motion conversion device. The machine body can also be in an integral form, and the corresponding connecting rod is changed into a split form.

Example two.

According to the figure 5, the embodiment provides a high-pressure compressor with a parallel hexagonal star structure, which comprises a machine body 01, a cylinder 02 and a rotary reciprocating motion conversion device 03, wherein the compressor adopts a parallel hexagonal star structure to perform five-stage compression, the rotary reciprocating motion conversion device comprises a piston 03-1, a connecting rod 03-2 and a single-throw crankshaft 03-3, the crankshaft 03-3 rotates to drive the piston 03-4 to perform reciprocating linear motion in the cylinder 02 through the connecting rod 03-2, six rows of cylinders 02 are uniformly arranged in parallel around the circumference of the rotating center of the crankshaft 03-3, and the included angle between two adjacent rows of cylinders 5 is 60 degrees; the centerlines of the six rows of cylinders 02 lie in different planes and are perpendicular to the center of the crankshaft 03-3 while intersecting the axis of rotation of the crankshaft 03-3. The cylinder 02 has five stages I, II, III, IV and V, which correspond to the five-stage pistons 03-1, and the high-efficiency and high-pressure compression of gas is realized by interstage cooling among the stages. The technical effect described in the first embodiment can be achieved by adjusting the piston mass to make the five-stage piston mass approximately equal. The cylinder head valve group, the driving device and the accessories of the compressor are not described too much, and the related points can refer to the existing piston compressor.

Although the present application has been described with reference to the preferred embodiments, it is not intended to limit the present application, and those skilled in the art can make variations and modifications without departing from the spirit and scope of the present application, therefore, the scope of the present application should be determined by the claims that follow.

Claims (10)

1. The utility model provides a six star piston compressors side by side, includes, organism, cylinder, rotatory reciprocating motion conversion equipment, drive arrangement which characterized in that:

the rotary reciprocating motion conversion device comprises a single-throw crankshaft, six pistons and six connecting rods for connecting the single-throw crankshaft and the six pistons; the six pistons are uniformly arranged around the rotation center of the single-throw crankshaft at intervals of 60 degrees, the reciprocating motion center lines of the six pistons are positioned on different planes, one ends of the six connecting rods are arranged on crank pins of the single-throw crankshaft in parallel, and the other ends of the six connecting rods are respectively connected to the six pistons; the six rows of cylinders are uniformly arranged around the rotating central axis of the rotating reciprocating motion conversion device at intervals of 60 degrees and are in one-to-one correspondence with the six pistons, and the central lines of the six rows of cylinders are positioned on different planes and are perpendicular to and intersected with the rotating central axis; wherein the six pistons reciprocate in the six cylinders; the cylinder and the single-throw crankshaft of the rotary reciprocating motion conversion device are arranged on the machine body, and the single-throw crankshaft of the rotary reciprocating motion conversion device is connected with the driving shaft of the driving device.

2. A parallel six-star piston compressor according to claim 1, wherein balancing weights are arranged at both ends of the single throw crankshaft, respectively.

3. The tandem six-star piston compressor as claimed in claim 1, wherein the single throw crankshaft is a split structure including two parts, a crank pin and a crank, the crank pin being detachably connected to the crank by a fastener.

4. The parallel six-star piston compressor as claimed in claim 1, wherein a support shaft diameter is provided in the middle of the single throw crankshaft.

5. A parallel six-star piston compressor as claimed in claim 1, wherein the connecting rod is connected to the crankshaft and the pistons by bearings using grease seals.

6. A parallel six-star piston compressor as claimed in claim 1, wherein: at least the part of the outer surface of the piston, which is in contact with the inner wall of the cylinder, is coated with a self-lubricating wear-resistant layer.

7. A parallel six-star piston compressor as claimed in claim 1, wherein: the surface of the inner wall of the cylinder is subjected to ceramic treatment.

8. A parallel six-star piston compressor as claimed in claim 1, wherein: the front end face and the rear end face of the machine body are provided with connecting holes for mounting a bearing and a driving device, and six side faces are provided with holes for mounting the air cylinder.

9. A parallel six-star piston compressor according to any of claims 1 to 8, wherein: the machine body is divided into two parts along the center of the rotary reciprocating motion conversion device, and each part is provided with a hole for mounting the air cylinder and a bearing hole.

10. A parallel six-star piston compressor as claimed in claim 1, wherein the compressor is a multi-stage compressor in which some or all of the pistons are stepped pistons, the mass of each piston assembly being approximately equal.

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