CN101865268B - Crank-round slider mechanism, crank shaft thereof and equipment using same - Google Patents

Abstract

A crank circular slider mechanism, comprising a circular slider, a reciprocating member, a crankshaft and a frame; the crankshaft includes a crank at both ends and a main journal between the two cranks, the crank and the main journal have a common axis of rotation, the axis is the rotation axis of the crankshaft; two coaxial crank pins protrude from the two ends of the main journal respectively, and extend to the end surface of the two cranks facing the main journal; the distance between the axes of the two crank pins and the rotation axis of the crankshaft is e; the circular slider has an eccentric circle hole; each crank pin is sleeved with two circular sliders with a phase difference of 180 degrees and solidly integrated, and the two circular sliders adjacent to the main journal have the same phase; the reciprocating parts are set on the guide rail on the frame Middle; each slider can be rotatably set in a slider accommodating hole of a reciprocating piece; the guide rails of the reciprocating piece corresponding to the sliders with the same phase are parallel; the reciprocating motion corresponding to the slider with a phase difference of 180 degrees The rails of the pieces are perpendicular to each other. The mechanism of the invention can improve the ability of the crankshaft to resist bending deformation, and further can effectively improve the stability of the mechanism. The invention additionally provides a crankshaft of the crank-circular slider mechanism and a device using the mechanism.

Description

A crank circular slider mechanism, its crankshaft, and equipment using the mechanism

technical field

The invention relates to a mechanism for mutual conversion between reciprocating motion and rotary motion, in particular to a crank circular slider mechanism. The invention also relates to a crankshaft of the crank circular slider mechanism and equipment using the mechanism.

Background technique

In conventional internal combustion engines and compressors, the conversion between the reciprocating motion of the piston and the rotational motion of the crankshaft is achieved by a crank-and-rod mechanism. However, due to the existence of the connecting rod, the internal combustion engine and compressor of the crank linkage mechanism have disadvantages such as bulky, heavy, and poor balance performance.

In order to solve the problems referred to above, the Chinese patent whose approval announcement date is January 13, 1988 and whose announcement number is CN85100358B discloses a kind of "crank circular slider reciprocating piston internal combustion engine". The date of examination and approval announcement is December 14, 1988, and the Chinese patent whose announcement number is CN85100359B discloses a kind of "crank circular slider reciprocating piston compressor". In the internal combustion engine and compressor disclosed in the Chinese patent, the crank-and-slider mechanism is used to replace the crank-link mechanism as a mechanism for converting reciprocating motion and rotary motion. Wherein, the crank circular slider mechanism includes a circular slider, a piston and a crankshaft; the circular slider is provided with an eccentric circular hole; and the piston seat of the piston is provided with a circular slider accommodating hole. When assembling, the circular slider is rotatably arranged in the accommodating hole of the circular slider; the crank pin of the crankshaft is rotatably assembled in the eccentric circular hole.

Take the internal combustion engine as an example below to illustrate the working mode of the above-mentioned crank circular slider mechanism. When working, the combustion gas in the combustion chamber expands and pushes the piston to move, and the piston drives the circular slider set therein to reciprocate, while the circular slider rotates in the piston at the same time, the combination of the reciprocating motion and the rotary motion makes The central axis of the eccentric circular hole on the circular slider rotates around the central axis of the crankshaft; and the central axis of the eccentric circular hole coincides with the axis of the crankpin of the crankshaft, so that the reciprocating motion of the piston and the rotational motion of the crankshaft can be realized. convert. When the compressor is working, the process is just the opposite.

In the technical solution disclosed in the above-mentioned Chinese patent, an internal gear transmission pair structure needs to be adopted to solve the problem of the active point. However, this structure is only suitable for a single-cylinder engine, and the dynamic balance performance is not ideal.

Based on this, the Chinese patent whose authorization announcement date is June 27, 2001 and whose authorization announcement number is CN1067741C discloses a "crank double circular slider reciprocating piston internal combustion engine". The circular sliders form a circular slider group, and the two circular sliders are respectively placed in the reciprocating parts whose reciprocating directions are perpendicular to each other. When working, the reciprocating parts perpendicular to each other can overcome the live point problem, and can convert their respective reciprocating inertial forces into centrifugal inertial forces, so as to facilitate their balance. Has a better balancing effect.

The Chinese patent with the authorized announcement date of June 27, 2001 and the authorized announcement number CN1067742C discloses a "crank multi-slider reciprocating piston internal combustion engine". In this internal combustion engine, there are three circular sliders, and the phase difference between adjacent circular sliders is It is also 180 degrees, thereby forming a group of circular sliders in which the circular sliders located in the middle and the circular sliders located at both ends have a phase difference of 180 degrees, and the phases of the two circular sliders located at both ends are the same. The circular sliders with the same phase are placed in the reciprocating parts parallel to the reciprocating direction, and the circular sliders with a phase difference of 180 degrees are respectively placed in the reciprocating parts perpendicular to the reciprocating direction.

For the mechanism of the circular slider group of three circular sliders, the reciprocating inertial forces perpendicular to each other can also be converted into centrifugal inertial forces and the problem of the live point of the single circular slider mechanism can be overcome. Moreover, compared with the mechanism of the double-circle slider group, the mechanism of the three-circle slider group can also balance the reciprocating inertia moment, and has a better balance effect.

However, because in the mechanism of the three-round slider group, three round sliders are arranged on the single-throw crankshaft, this makes the span of the crank pin of the single-throw crankshaft larger. When this mechanism is applied to an internal combustion engine or a compressor, the crank pin will be bent and deformed. Especially with the continuous improvement of the internal combustion engine, the gas pressure acting on the piston is increasing, and the diesel internal combustion engine adopting supercharging, intercooling, high-pressure common rail and other technologies has a higher maximum burst pressure and a higher speed. The pressure on the piston and the reciprocating inertial force of the piston will act on the crank pin of the crankshaft, especially the mass of the dynamic balance slider is the sum of the two piston masses, and the reciprocating inertial force generated by it is greater, which is more serious. Bending deformation of the crankpin. And improve the intensity of crank pin by enlarging the method for crank pin diameter, be difficult to implement owing to being subjected to the restriction of the cooperation relation of crank pin and circular slider, piston and the limitation of whole mechanism overall quality again. Thereby, the application of the three-circular slider crank circular slider mechanism in high-strength demand internal combustion engines, compressors and other equipment is limited.

Contents of the invention

The invention provides a crank circular slider mechanism to solve the problem of bending and deformation of the crank pin of the crank circular slider mechanism of the existing three circular sliders. The invention further provides a crankshaft of the crank-circular-slider mechanism and equipment using the mechanism.

The present invention provides a crank circular slider mechanism, comprising a circular slider, a reciprocating member, a crankshaft and a frame supporting the mechanism;

The crankshaft includes cranks at both ends and a main journal between the two cranks. The crank and the main journal have a common rotation axis, which is the rotation axis of the crankshaft. The crank and the main journal are rotatably supported on On the frame; the two crank pins respectively extend from the two opposite end surfaces of the main journal, and extend to the end surfaces of the two cranks facing the main journal, and are fixedly connected with the crank; the two crank pins have a common and parallel the axis of the axis of rotation of the crankshaft, and the axis is offset from the axis of rotation of the crankshaft by a distance e;

The circular slider has an eccentric circular hole with an eccentricity of e, which is used for the crank pin to pass through the eccentric circular hole of the circular slider, so that the circular slider can be rotatably socketed on the crank pin; Two circular sliders with a phase difference of 180 degrees and fixed as one are connected, and the two circular sliders of adjacent main journals have the same phase;

The reciprocating parts are set in the reciprocating guide rails on the frame; the reciprocating parts are provided with circular slider accommodating holes for accommodating the circular sliders; each circular slider can be rotatably arranged on a reciprocating part The reciprocating guide rails of the reciprocating parts corresponding to the circular sliders with the same phase are parallel; the reciprocating guide rails of the reciprocating parts corresponding to the circular sliders with a phase difference of 180 degrees are perpendicular to each other.

Optionally, the two cranks and the crank pin are in a split structure, an eccentric mounting hole is provided at the end of the crank facing the crank pin, and the end of the crank pin away from the main journal is inserted into the eccentric mounting hole , and the crank pin is fixed as a whole.

Optionally, the two crank pins are integrated, which is called integral crank pin; the main journal is provided with eccentric holes penetrating both ends thereof, and the distance between the axis of the eccentric hole and the rotation axis of the main journal is e; The integral crank pin passes through the eccentric hole and is fixed integrally with the main journal.

Optionally, the reciprocating parts corresponding to the circular sliders of two adjacent cranks are pistons, and the circular sliders are called working circular sliders; the reciprocating parts corresponding to the two circular sliders of adjacent main journals are dynamic balance sliders, and the circular sliders It's called a balance slider.

Preferably, the sum of the masses of the two dynamic balance sliders is equal to the sum of the masses of the two pistons.

Preferably, the mass of the balancing circular slider located on the same side of the main journal is the same as that of the working circular slider, and the center of gravity is symmetrical with respect to the centers of the eccentric circular holes of the two circular sliders.

Optionally, a synchronization mechanism for making the two cranks rotate synchronously is also included.

Optionally, the synchronous mechanism includes a synchronous shaft whose axis is parallel to the rotational axis of the crankshaft, a synchronous shaft with first synchronous gears arranged at both ends, and two second synchronous gears respectively fixed and coaxial with the two cranks; A synchronous gear meshes with the corresponding second synchronous gear, or respectively meshes with the corresponding first synchronous gear and the second synchronous gear through an intermediate transmission wheel.

The present invention also provides a crankshaft applied to any one of the crank circular slider mechanisms described above, the crankshaft includes cranks at both ends and a main journal located between the two cranks, the crank and the main journal have a common axis of rotation , the rotating shaft is the rotating shaft of the crankshaft; the two crank pins respectively extend from the two opposite end faces of the main journal and extend to the end faces of the two cranks facing the main journal, and are fixedly connected with the crank; the two crank pins have an axis common to and parallel to the axis of rotation of the crankshaft and offset by a distance e from the axis of rotation of the crankshaft.

Optionally, the two crank pins of the crankshaft are integrated, called integral crank pins; the main journal is provided with an eccentric hole penetrating through its two ends, and the distance between the axis of the eccentric hole and the rotational axis of the main journal is e ; The integral crank pin passes through the eccentric hole and is fixed as a whole with the main journal.

The present invention also provides a device, which is an internal gas pump, comprising any one of the above-mentioned crank circular slider mechanisms; wherein, at least one reciprocating member on a crank pin of the crankshaft is an internal combustion engine piston, and the internal combustion engine piston The corresponding reciprocating member guide rail is an internal combustion engine cylinder; at least one reciprocating member on the other crank pin of the crankshaft is an air compressor piston, and the reciprocating member guide rail corresponding to the air compressor piston is an air compressor cylinder.

The present invention also provides a device, which is an internal combustion engine, and includes any one of the crank-circle-slider mechanisms described above.

The present invention also provides a device, which is a compressor, and includes any one of the crank and circular slider mechanisms described above.

Compared with the prior art, the crankshaft of the crank circular slider mechanism of the present invention has two cranks located at both ends, and also has a main journal located in the middle; the main journal divides the crank pin of the crankshaft into two sections, which can be respectively The first crank pin and the second crank pin; the cranks at both ends can be directly supported on the frame, and the main journal can also be rotatably supported on the frame; so that the crankshaft of the mechanism can be supported at three points, and each crank Compared with the existing two-point support structure with only cranks at both ends, the length of the crank pin is shortened, that is, the span of the crank pin is reduced, thereby greatly improving the ability of the crankshaft to resist bending deformation, and thus effectively improving the mechanism. stability. Moreover, the dynamic balance slider is divided into two, and the quality of each dynamic balance slider is less than that of a single piston or the mass of the two is the same, so that the reciprocating inertial force of the dynamic balance slider is greatly reduced, greatly improving The force condition of a single crankpin is shown.

In addition, in order to obtain a better balance effect, one can set the sum of the masses of the two dynamic balance sliders to be equal to the sum of the masses of the two pistons; and the masses of the four reciprocating parts are equal, and the center of gravity falls on its central axis Above; 2. The mass of the two circular sliders located on the same side of the main journal can be set to be the same, and the center of gravity is symmetrical to the center of the eccentric circular hole of the two circular sliders; when the above two conditions are met, the best balance effect can be achieved, and not only the reciprocating inertia can be transformed The force is a centrifugal inertia force, and can balance the reciprocating inertia moment of the mechanism.

In the internal gas pump of the present invention, the crankshaft of the internal combustion engine and the crankshaft of the air compressor are coaxial, and the power can be directly transmitted to the air compressor, without the need for belts or chains to transmit power between the two like traditional air pumps, which can avoid Reduce power loss, improve efficiency, and also make the whole mechanism run stably, with compact structure, reduced volume and reduced weight.

Description of drawings

Fig. 1 is the schematic sectional view of the embodiment of the crank circular slider mechanism provided by the present invention;

Fig. 2 is the schematic diagram of the cross-section of Fig. 1 along AA';

FIG. 3 is a schematic diagram of the crankshaft in FIG. 1 .

Detailed ways

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. However, the present invention can be implemented in many other ways different from those described here, and those skilled in the art can make similar extensions without violating the connotation of the present invention, so the present invention is not limited by the specific implementations disclosed below.

The crank circular slider mechanism of the present invention will be described in detail below in conjunction with the accompanying drawings.

Fig. 1 is a schematic cross-sectional view of an embodiment of a crank circular slider mechanism provided by the present invention; Fig. 2 is a schematic cross-sectional view of Fig. 1 taken along AA '; Fig. 3 is a schematic diagram of the crankshaft in Fig. 1 .

Please refer to FIG. 1 , in an embodiment of the present invention, the crank circular slider mechanism includes a crankshaft 1 , a circular slider, a reciprocating member and a frame supporting the mechanism.

The crankshaft 1 has two crank pins, and there are four sliders, namely: the first slider 2-1a, the second slider 2-1b, the third slider 2-2b and the fourth slider 2 -2a. Correspondingly, there are four reciprocating parts, which are respectively the first reciprocating part 3a, the second reciprocating part 4a, the third reciprocating part 4b and the fourth reciprocating part 3b.

FIG. 3 is a structural schematic diagram of the crankshaft 1 shown in FIG. 1 .

Please refer to FIG. 3 , the crankshaft 1 in the embodiment of the present invention includes a first crank 1-1a and a second crank 1-1b at two ends, and a crank 1-1a between the first crank 1-1a and the second crank 1-1b Main journal 1-2. Wherein, the first crank 1-1a, the second crank 1-1b and the main journal 1-2 are all in the shape of flat cylinders. The radial cross-sectional diameters of the three can be the same or different. In this embodiment, the radial cross-sectional diameters of the three are the same as an example for illustration.

The first crank 1-1a, the second crank 1-1b and the main journal 1-2 can provide three-point support for the crankshaft 1 by cooperating with the bearings arranged on the frame through their outer peripheral surfaces. And the first crank 1-1a, the second crank 1-1b and the main journal 1-2 can all rotate in their corresponding bearings and their rotation axes are located on the same straight line, that is, they have the same rotation axis, and the rotation axis is The axis of rotation of the crankshaft.

The first crank pin 1-3a and the second crank pin 1-3b protrude from two opposite end surfaces of the main journal 1-2 respectively, and extend to the ends of the first crank 1-1a and the second crank 1-1b. The inner end surface (that is, the end surface of the crank facing the main journal 1-2) is solidly integrated with the first crank 1-1a and the second crank 1-1b.

Wherein, the first crank pin 1-3a and the second crank pin 1-3b are two identical cylindrical shaft segments. The axes of the two crank pins are on the same straight line, that is, they have a common axis, which is parallel to the rotation axis of the crankshaft and deviates from the rotation axis of the crankshaft by a certain distance e, which is generally equal to the eccentricity of the circular slider The eccentricity of the circular hole.

In addition, the radial cross-sectional diameter of the first crank pin 1-3a and the second crank pin 1-3b is smaller than the radial cross-sectional diameter of any one of the cranks mentioned above, and is also smaller than the radial cross-sectional diameter of the main journal 1-2 diameter. Therefore, the outer peripheral surfaces of the two crank pins are completely enclosed within or tangent to the outer peripheral surfaces of the crank and the main journal. Of course, it is also possible to make the crank pin overlap with the end face of the crank or the main journal, which will not be repeated here.

The first crank pin 1-3a and the second crank pin 1-3b are integrally formed with the main journal 1-2. The first crank pin 1-3a, the first crank 1-1a, the second crank pin 1-3b and the second crank 1-1b are all split structures, that is, the first crank 1-1a and the second crank 1-1b are all split structures. One end of the two cranks 1-1b facing the crank pin is provided with an eccentric mounting hole, and the ends of the first crank pin 1-3a and the second crank pin 1-3b away from the main journal 1-2 are inserted into the corresponding eccentric mounting holes, And it is fixed and assembled as a whole by fastening bolts. By arranging the split crank and the crank pin, it is convenient for the one-piece round slider to be fitted on the crank pin, that is, the assembly of the mechanism is facilitated. And when the circular slider is a split structure, the crank and the crank pin can also be of an integrated structure.

In addition, for split cranks and crank pins, a positioning structure is also required when assembling the two. To locate the two in the circumferential direction and the axial direction, the positioning pin can be used for the circumferential positioning, and the notch can be used for the axial positioning. Let me repeat them one by one. In addition, the ends where the first crank 1-1a and the second crank 1-1b are assembled can also be taper ends, and the eccentric mounting holes on the corresponding cranks also have matching taper surfaces, and the taper between the two Face fit facilitates torque transmission.

In addition, when the crank and the corresponding crank pins are of a separate structure, the first crank pin 1-3a and the second crank pin 1-3b can also be of an integral structure, called integral crank pins. The main journal 1-2 is provided with an eccentric hole penetrating both ends thereof, and the axis of the eccentric hole deviates from the rotation axis of the main journal 1-2 by a distance e. The integral crank pin passes through the eccentric hole and is fixed integrally with the main journal 1-2. In a preferred situation, the integral crank pin protrudes the same length at both ends of the main journal 1-2. For this structure, a positioning structure is also required between the integral crank pin and the main journal 1-2. I won't go into details here.

Please continue to refer to Fig. 1 and refer to Fig. 2, the four circular sliders described: the first circular slider 2-1a, the second circular slider 2-1b, the third circular slider 2-2b and the fourth circular slider 2-2a The structure can be the same, and each circular slider has an eccentric circular hole, and its eccentricity can be e. The crank pin of the crankshaft 1 can pass through the eccentric circular hole of the slider, and the slider is rotatably sleeved on the crank pin.

In this embodiment, the phase difference between the first circular slider 2-1a and the second circular slider 2-1b is set at 180 degrees, and they are fixedly assembled together, and the eccentric circular holes of the two circular sliders are aligned, and the crank pin 1-3a passes through its eccentric circular hole. The third circular slider 2-2b and the fourth circular slider 2-2a are fixed on the crank pin 1-3b in the same manner as the first circular slider 2-1a and the second circular slider 2-1b. And the phases of the second circular slider 2-1b and the third circular slider 2-2b adjacent to the main journal 1-2 are the same. Wherein, among the four circular sliders, the two circular sliders arranged on the same crank pin can be fixed by two pins (pins 2-1-1a and 2-1-2a as shown in Figure 2) Assembled as a whole, the Chinese patent with the authorized announcement date of June 27, 2001 and the authorized announcement number CN1067741C discloses a "crank double-circular slider reciprocating piston internal combustion engine", which discloses that the two circular sliders are fixed and assembled with a phase difference of 180 structure, which will not be repeated here. For a single circular slider, it can have various structures, for example, it can also be provided with a structure that changes the distribution of the center of mass, such as a weight-reducing hole, a weight-reducing groove, etc. oil circuit, etc. All the structures of the slider structure in the Chinese patent mentioned in the above background technology can be applied to the crank slider mechanism of the present invention. Of course, the slider structure applied to the present invention is not limited thereto, as long as it has an eccentric circular hole and The structure of the outer peripheral surface matched with the accommodating hole of the piston circular slider can be applied to the crank circular slider mechanism of the present invention.

The four reciprocating parts: respectively the first reciprocating part 3a, the second reciprocating part 4a, the third reciprocating part 4b and the fourth reciprocating part 3b, each reciprocating part is arranged on the frame In the guide rail of the reciprocating member, each reciprocating member is provided with a circular slider accommodating hole for accommodating the above-mentioned circular slider. Each circular slider can be rotatably arranged in a reciprocating member. In this embodiment, the first circular slider 2-1a is arranged in the first reciprocating member 3a, the second circular slider 2-1b is arranged in the second reciprocating member 4a, and the third circular slider 2 -2b is arranged in the third reciprocating member 4b, and the fourth circular slider 2-2a is arranged in the fourth reciprocating member 3b. The reciprocating guide rails of the first reciprocating member 3a and the fourth reciprocating member 3b are parallel, that is, the two reciprocating directions are parallel; the reciprocating guide rails of the second reciprocating member 4a and the third reciprocating member 4b are parallel. parallel; and the reciprocating member guide rails of the first reciprocating member 3a and the second reciprocating member 4a are perpendicular to each other.

The four reciprocating parts may be pistons, dynamic balance sliders or other reciprocating parts.

In this embodiment, the first reciprocating member 3a and the fourth reciprocating member 3b are pistons, and are double-acting pistons. Of course, the pistons can also be single-acting pistons; The round slider housed in it) is also called the working round slider.

The second reciprocating member 4 a and the third reciprocating member 4 b are dynamic balance sliders, as shown in FIG. 2 , and their corresponding circular sliders can be called balanced circular sliders. When the mechanism is working, the reciprocating direction of the dynamic balance slider is perpendicular to the reciprocating direction of the piston, and its main function is to convert the reciprocating inertial force of the reciprocating parts moving perpendicularly to each other into centrifugal inertial force, so as to facilitate its alignment. Balanced, and this structure can also overcome the problem of live spots.

In addition, in order to obtain a better balance effect, one can set the sum of the masses of the two dynamic balance sliders to be equal to the sum of the masses of the two pistons; and the masses of the four reciprocating parts are equal, and the center of gravity falls on its central axis Two can be set to be positioned at the same side of the main journal two circular sliders (balanced circular sliders and working circular sliders in this embodiment) have the same quality, and the center of gravity is symmetrical with respect to the center of the eccentric circular holes of the two circular sliders. When the above two conditions are met, the best balance effect can be achieved, not only can the reciprocating inertial force be converted into centrifugal inertial force, but also the reciprocating inertial moment of the mechanism can be balanced.

In the above embodiment, the crankshaft 1 of the crank-slider mechanism has two cranks: a first crank 1-1a and a second crank 1-1b at both ends, and a main journal 1-2 in the middle. The main journal 1-2 divides the crank pin of the crankshaft 1 into two sections, namely a first crank pin 1-3a and a second crank pin 1-3b. The first crank 1-1a and the second crank 1-1b can be directly supported on the frame, corresponding to the front and rear bearings on the frame, and the main journal 1-2 is also rotatably supported on the frame. Thereby, the crankshaft can be supported by three points, and each crank pin is shortened in length compared to the existing two-point support structure with only two ends of the crank pin, that is, the span of the crank pin is reduced, thereby effectively improving the The ability of the crankshaft to resist bending deformation can effectively improve the stability of the mechanism. Moreover, the dynamic balance slider is divided into two, and the quality of each dynamic balance slider is less than that of a single piston or the quality of the two is the same, so that the reciprocating inertial force of the dynamic balance slider is greatly reduced, greatly improving The force condition of a single crankpin is shown.

In addition, the mechanism may also include a synchronous mechanism, specifically, the synchronous mechanism includes a synchronous shaft whose axis is parallel to the rotation axis of the crankshaft, a synchronous shaft with first synchronous gears at both ends, and two coaxial shafts fixed and coaxial with the two cranks respectively. a second synchronous gear; the first synchronous gear meshes with the corresponding second synchronous gear, or meshes with the corresponding first synchronous gear and the second synchronous gear respectively through an intermediate transmission wheel. The agency can improve coordination and synchronicity when the agency works.

In addition, the present invention also provides a device, specifically, the internal combustion engine can also be a compressor. This device applies the crank-circle-slider mechanism of the above-mentioned embodiments.

In addition, the present invention also provides a device, which is specifically an internal gas pump, and the device includes the crank and slider mechanism of the above-mentioned embodiment; wherein, at least one reciprocating member on a crank pin of the crankshaft is a piston of an internal combustion engine , the reciprocating member guide rail corresponding to the piston of the internal combustion engine is an internal combustion engine cylinder; at least one reciprocating member on the other crank pin of the crankshaft is an air compressor piston, and the reciprocating member guide rail corresponding to the air compressor piston is an air cylinder. Compressor cylinder.

For example, the first reciprocating part 3a in Fig. 1 can be an internal combustion engine piston, the second reciprocating part 4a and the third reciprocating part 4b are dynamic balance sliders, and the fourth reciprocating part 3b is an air compressor piston. The mechanism is assembled in the body to form a direct-connected internal gas pump.

Wherein, the air compressor piston and the internal combustion engine piston may be single-acting pistons or double-acting pistons.

In the internal gas pump, the crankshaft of the internal combustion engine and the crankshaft of the air compressor are coaxial, so that the internal combustion engine and the air compressor are directly connected, and the power can be directly transmitted to the air compressor, without the need for a belt or chain between the two as in the traditional air pump. This can avoid power loss, improve efficiency, and also make the whole mechanism run stably, with compact structure, reduced volume and reduced weight.

Although the present invention is disclosed as above with preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make possible changes and modifications without departing from the spirit and scope of the present invention. Therefore, the present invention The scope of protection should be based on the scope defined by the claims of the present invention.

Claims (13)

1. a circular slider-crank mechanism is characterized in that: comprise smooth block, reciprocating part, bent axle and the frame that supports this mechanism;

Said bent axle comprises that said crank and main journal have common axis of rotation at the crank at two ends and the main journal between two cranks, and this running shaft is the crankshaft rotating axle, and said crank and main journal rotary supporting are on frame; Two crank pins are extended by two opposing end surfaces of this main journal respectively, and extend to said two cranks towards the main journal end face, are fixedly connected with said crank; Described two crank pins have jointly and are parallel to the axis of said crankshaft rotating axle, and the distance of the said crankshaft rotating axle of this axis runout is e;

Said smooth block has the eccentric circular hole that throw of eccentric is e, is used for the eccentric circular hole that crank pin passes said smooth block, makes that smooth block is rotatable to be socketed on the crank pin; On each crank pin, all be socketed with two phase differences and be the smooth block that 180 degree are provided with and are solidified as a whole, two smooth blocks of adjacent main journal have identical phase place;

Reciprocating part is arranged in the to-and-fro motion guide rail on the frame; Reciprocating part is provided with circular slider accommodation hole, is used for ccontaining described smooth block; Each smooth block is all rotatable to be arranged in the circular slider accommodation hole of a reciprocating part; The to-and-fro motion guide rail of the reciprocating part that the smooth block that phase place is identical is corresponding is parallel; The to-and-fro motion guide rail that phase difference is the corresponding reciprocating part of the smooth block of 180 degree is vertical each other.

2. circular slider-crank mechanism according to claim 1; It is characterized in that: said two cranks and said crank pin are split-type structural; Be provided with eccentric mounting hole at said crank towards an end of crank pin; Crank pin inserts in the said eccentric mounting hole away from the end of said main journal, is fixed as one with this crank pin.

3. circular slider-crank mechanism according to claim 2 is characterized in that: said two crank pins are an integral body, are called the integrated type crank pin; Main journal is provided with the eccentric opening that runs through its both ends of the surface, and the distance of said this main journal running shaft of eccentric opening axis runout is e; Said integrated type crank pin passes said eccentric opening, and is fixed as one with this main journal.

4. circular slider-crank mechanism according to claim 1 is characterized in that: the reciprocating part that the smooth block of adjacent two cranks is corresponding is a piston, and this smooth block is called the work smooth block; The reciprocating part that two smooth blocks of adjacent main journal are corresponding is a dynamic balance slide block, and this smooth block is called the balance smooth block.

5. circular slider-crank mechanism according to claim 4 is characterized in that: the quality sum of said two dynamic balance slide blocks equals the quality sum of two-piston.

6. according to claim 4 or 5 described circular slider-crank mechanisms, it is characterized in that: be positioned at the balance smooth block and the identical in quality of smooth block of working of said main journal homonymy, center of gravity is with respect to the center symmetry of two smooth block eccentric circular holes.

7. circular slider-crank mechanism according to claim 1 is characterized in that: also comprise being used to make the two cranks lazy-tongs of rotation synchronously.

8. circular slider-crank mechanism according to claim 7 is characterized in that: said lazy-tongs comprise axis parallel with said crankshaft rotating axle, two ends are provided with the synchronizing shaft of first synchromesh gear and fix with two cranks respectively and two second coaxial synchromesh gears; Said first synchromesh gear is meshed with corresponding second synchromesh gear, perhaps is meshed with corresponding first synchromesh gear and second synchromesh gear respectively through middle drive wheel.

9. bent axle that is applied to the arbitrary described circular slider-crank mechanism of claim 1 to claim 8; It is characterized in that: said bent axle comprises at the crank at two ends and the main journal between two cranks; Said crank and main journal have common axis of rotation, and this running shaft is the crankshaft rotating axle; Two crank pins are extended by two opposing end surfaces of this main journal respectively and extend to said two cranks towards the main journal end face, are fixedly connected with said crank; Described two crank pins have jointly and are parallel to the axis of said crankshaft rotating axle, and the distance of the said crankshaft rotating axle of this axis runout is e.

10. bent axle according to claim 9 is characterized in that: said two crank pins are an integral body, are called the integrated type crank pin; Main journal is provided with the eccentric opening that runs through its both ends of the surface, and the distance of said this main journal running shaft of eccentric opening axis runout is e; Said integrated type crank pin passes said eccentric opening, and is fixed as one with this main journal.

11. an equipment, this equipment is the internal combustion air pump, it is characterized in that: comprise the arbitrary described circular slider-crank mechanism of aforesaid right requirement 1 to claim 8; Wherein, at least one reciprocating part on the crank pin of said bent axle is an internal combustion engine, and the reciprocating part guide rail corresponding with this internal combustion engine is cylinder of internal-combustion engine; At least one reciprocating part on another crank pin of said bent axle is an air-compressor piston, and the reciprocating part guide rail corresponding with this air-compressor piston is the air compressor cylinder.

12. an equipment, this equipment is internal-combustion engine, it is characterized in that: comprise the arbitrary described circular slider-crank mechanism of aforesaid right requirement 1 to claim 8.

13. an equipment, this equipment is compressor, it is characterized in that: comprise the arbitrary described circular slider-crank mechanism of aforesaid right requirement 1 to claim 8.

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