CN101737297A - Reciprocating-piston type oil-less air compressor - Google Patents

Abstract

The invention relates to a reciprocating-piston type oil-less air compressor. In the invention, a piston of a compressor is fastened with a connecting rod or integrally manufactured with the connecting rod; and the piston is arranged in an air cylinder and reciprocates and swings relative to the air cylinder. The reciprocating-piston type oil-less air compressor is characterized in that: the air cylinder adopts an offset structure, which means the axial line of the air cylinder is not intersected with the axial line of a crankshaft, so the offset angle of the piston relative to the air cylinder is reduced in the compression stroke, and the lateral pressure and panting strength of the piston on the air cylinder and the abrasion loss of a sealing ring or a sealing rubber cup are reduced; besides, the oval deformation of the sealing ring or the sealing rubber cup is reduced, so the fatigue state thereof is relieved and the screech which is generated by the leakage at an oval gap and the escape of gas is reduced; and moreover, structures such as a closed crankcase structure, a crankcase air inlet soundproofing chamber, an air inlet channel and the like are adopted for effectively reducing the induction noise and the induction jetting noise and an exhaust soundproofing housing is adopted for reducing the exhaust noise, so the reciprocating-piston type oil-less air compressor can be used for manufacturing the air compressor, an air pump, a vacuum pump or a fluid pump.

Description

Reciprocating-piston type oil-less air compressor

Technical field

The invention belongs to the Compressor Technology field, relate to reciprocating-piston air compressor, particularly reciprocating-piston type oil-less air compressor.

Background technique

In the existing air compressor, a kind of reciprocating-piston type oil-less air compressor is arranged, it includes cylinder, cylinder head, piston, connecting rod, crank pin, bent axle, valve seat and crankcase, different with general Reciprocting piston compressor, the piston of such compressor and connecting rod adopt is to be fastenedly connected or to be the structural type of integral production, therefore piston also has oscillating motion with respect to the existing to-and-fro motion of cylinder in the course of the work, owing to be fitted with seal ring or the sealing cup of making of self-enrichment material on the piston, therefore such compression function provides the pressurized air of oil-containing hardly, and crankcase need not to store lubricant oil, so operation and maintenance is very convenient.

Up to now, above-mentioned compressor adopts zero offset air cylinder structure layout bar none, that is the shaft center line of the shaft axis of cylinder and bent axle is the structural type that intersects vertically, and is unquestionable, and this is easily for making and detecting.But, the zero offset air cylinder structure still has deficiency, mainly show: the seal ring of compressor or sealing cup operating life are shorter, the operational noise of compressor is also bigger in addition, trace it to its cause is that the compression stroke deflection angle and the suction stroke deflection angle of piston is the symmetrical distribution state, this topology layout limits its compressor that is difficult to take into account the different designs target call, specifically have two drawbacks: 1) the zero offset air cylinder structure is unfavorable for the compressor that those require the long lifetime design, this is because structure is limit and made the compression stroke deflection angle of piston can not do little, in other words piston has bigger angle of inclination with respect to cylinder when compression stroke, this has increased the side pressure active force of piston to cylinder on the one hand, cause seal ring or sealing cup to wear and tear too early, highpressure forces seal ring or sealing cup generation ovalizing deflection amplitude in the process of pasting cylinder wall surface that outwards expands bigger on the other hand, causes seal ring or sealing cup premature fatigue to be damaged; 2) the zero offset air cylinder structure is unfavorable for the compressor that those require Design of Low Noise, it is same because the piston compression stroke deflection angle is relatively large, the result works as compressor and is under the highpressure background of compression stroke, aggravated the bounce dynamics of piston on the one hand to cylinder, cause more serious mechanical impact noise, increased the oval gap leakage between piston and the cylinder on the other hand, caused pressurized gas ease to be escaped and send the pneumatic noise that screams.

Summary of the invention

Deficiency at existing zero offset air cylinder structure oil-free air compressor existence, the present invention proposes a kind of reciprocating-piston type oil-less air compressor, one of purpose is to reduce the wearing and tearing and the fatigue damage of seal ring or sealing cup, to prolong the work working life of compressor; Two of purpose is to alleviate the bounce intensity of piston to cylinder, to reduce the mechanical beat noise of compressor; Three of purpose is to reduce the oval slot leakage of pressurized gas break-through and the gas ease that the produces sound of escaping to scream, to reduce the gas flow noise of compressor.

The object of the present invention is achieved like this:

Reciprocating-piston type oil-less air compressor, comprise: cylinder, piston, connecting rod, bent axle and crankcase, one end of described cylinder is connected with cylinder head or valve seat, the other end of cylinder is connected with crankcase, described piston and connecting rod adopt and are fastenedly connected or piston and connecting rod are integral production, piston is positioned in the cylinder and the reciprocating and oscillating motion with respect to cylinder, the crankshaft rotating shaft axis of described bent axle has an offset distance at a distance of the cylinder shaft axis of cylinder, form positive bias air cylinder structure or negative bias air cylinder structure, that is the crankshaft rotating shaft axis of the cylinder shaft axis of described cylinder and described bent axle is non-intersect.

Above-mentioned cylinder, piston, connecting rod and accessory respectively have one or more.

Above-mentioned piston is split type piston or is one-piece piston.

Above-mentioned crankcase is closed crankcase structure.

Above-mentioned crankcase constitutes crankcase intake noise reduction chamber.

Above-mentioned crankcase intake noise reduction chamber is connected with ambient atmosphere by suction port; Perhaps crankcase intake noise reduction chamber is connected with ambient atmosphere by gas-entered passageway and suction port.

Above-mentioned suction port place is provided with breather check valve; Perhaps be provided with one-way valve at the place, air outlet of gas-entered passageway; Perhaps in gas-entered passageway, be provided with muffler material or filtering material.

The crankshaft rotating shaft axis of above-mentioned bent axle is less than or equal to radius of crankshaft with respect to the offset distance or the title cylinder offset amount of the cylinder shaft axis of cylinder.

Above-mentioned valve seat or cylinder head are provided with the exhausting silencer cover.

The work bottom surface of the top work surface of above-mentioned piston, valve seat or cylinder is plane or class plane.

Above-mentioned cylinder is that normotopia cylinder and piston are the loxosis piston; Perhaps described cylinder is that loxosis cylinder and piston are the normotopia piston; Perhaps described cylinder is that loxosis cylinder and piston are the loxosis piston.

The work bottom surface of the top work surface of above-mentioned piston, valve seat or cylinder is sphere.

The purposes of reciprocating-piston type oil-less air compressor can be used for making air compressor or gas pump or vacuum pump or fluid pump.

The outstanding compared to existing technology advantage of the present invention is:

1, the present invention adopts the positive bias air cylinder structure, piston is with respect to the swing angle of cylinder in the time of can reducing compression stroke, make that the motion of piston approaches straight reciprocating motion more in compression stroke, can reduce the side pressure of piston on the one hand to cylinder, not only reduced the wear extent of seal ring or sealing cup thus, and reduced the bounce intensity of piston cylinder; Ovalizing deflection amplitude owing to compression stroke is reduced on the other hand, not only help improving the fatigue resistance of seal ring or sealing cup, but also can reduce the leakage rate of pressurized gas by oval slit, so can improve compressor work working life, reduce the mechanical beat noise of compressor and reduce the pressurized gas ease noise that screams when escaping.

2, the present invention adopts the negative bias air cylinder structure, based on the compressor of pursuing Design of Low Noise, has positive effect for those, this is because the negative bias air cylinder structure can reduce the pairing crankshaft rotating angle of compressor compresses stroke, in other words, the compression stroke time corresponding shortens or Piston Compression speed accelerates, can reduce the time of gas leakage thus, and can reduce leakage rate by the formed throttle effect of the quickening of piston motion, and can remedy because of the piston swing angle increases the leakage loss produces, escape and escape the noise that screams that produced so can reduce the compressor pressurized gas.

3, adopt the multi cylinder structure can under the prerequisite of same displacement and same cylinder structural parameter, reduce the working speed of compressor significantly, not only can reduce the average movement velocity of piston thus and reduce the wear extent of seal ring or sealing cup, and various mechanical vibration and knock the mechanical noise that is caused and also descended significantly, gas flow speed descends and also can reduce the suction noise of compressor in addition.

4, the present invention changes crankcase into closed crankcase structure by traditional Open architecture, and forms crankcase intake noise reduction chamber, can shield and absorb thus from the gas ease of the oval gap leakage generation between piston and the cylinder to escape the pneumatic noise that screams; By breather check valve and gas-entered passageway are set, can reduce air inlet thus and regurgitate noise; By being set, the exhausting silencer cover can reduce the exhaust sound that the exhaust of compressor pulse feature causes.

Description of drawings

Fig. 1 is the transverse section schematic diagram of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts the positive bias cylinder;

Fig. 2 is the transverse section schematic diagram of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts the negative bias cylinder;

Fig. 3 be reciprocating-piston type oil-less air compressor of the present invention when adopting positive bias cylinder and cylinder offset amount less than radius of crankshaft piston be in the kinematic sketch of mechanism of four limit position states such as top dead center, maximum inhale stroke deflection angle, lower dead center and maximum compression stroke deflection angle respectively with respect to cylinder;

Fig. 4 is the kinematic sketch of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts two cylinders of V-type and dual-piston structure;

Fig. 5 is the kinematic sketch of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts traditional open crankcase structure;

Fig. 6 is the axonometric drawing that reciprocating-piston type oil-less air compressor of the present invention adopts traditional open crankcase structure;

Fig. 7 is the side view that reciprocating-piston type oil-less air compressor of the present invention shown in Figure 6 adopts traditional open crankcase structure;

Fig. 8 is the kinematic sketch of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts closed crankcase structure;

Fig. 9 is the axonometric drawing that reciprocating-piston type oil-less air compressor of the present invention adopts closed crankcase structure;

Figure 10 is the side view that reciprocating-piston type oil-less air compressor of the present invention shown in Figure 9 adopts closed crankcase structure;

Figure 11 is that reciprocating-piston type oil-less air compressor of the present invention adopts crankcase intake noise reduction chamber and exhausting silencer cover and suction port is opened in drawing in side sectional elevation on the crankcase;

Figure 12 is that reciprocating-piston type oil-less air compressor of the present invention adopts crankcase intake noise reduction chamber and exhausting silencer cover and adopts suction port and drawing in side sectional elevation that gas-entered passageway is connected with ambient atmosphere;

Figure 13 is the kinematic sketch of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts normotopia cylinder and loxosis piston layout;

Figure 14 is the kinematic sketch of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts loxosis cylinder and normotopia piston layout;

Figure 15 is the kinematic sketch of mechanism that reciprocating-piston type oil-less air compressor of the present invention adopts loxosis cylinder and loxosis piston layout;

Figure 16 is that reciprocating-piston type oil-less air compressor pistons work end face of the present invention, valve seat or cylinder operation bottom surface are the kinematic sketch of mechanism of spheric structure.

The implication of the subalphbet that occurs in the above-mentioned accompanying drawing is as follows:

O1: the shaft center line of bent axle is called the crankshaft rotating shaft axis;

O2: the shaft axis of cylinder is called the cylinder shaft axis;

O3: the shaft axis of connecting rod bottom-end bearing and crank pin is called crank pin axle center line;

E: the cylinder offset amount refers to the distance of crankshaft rotating shaft axis O1 apart from cylinder shaft axis O2;

R: crank pin axle center line O3 also is called radius of crankshaft around the turning radius of crankshaft rotating shaft axis O1;

P: valve seat or cylinder head work bottom surface, general reference valve seat work bottom surface (this moment only valve seat directly in the face of the pistons work end face), cylinder head work bottom surface (this moment only cylinder head directly in the face of the pistons work end face and valve seat is inclusive in the cylinder head or valve seat and cylinder head integral production), the various set of valve seat work bottom surface and cylinder head work bottom surface sum (valve seat and cylinder head are faced the top work surface of piston simultaneously at this moment), can abbreviate the work bottom surface as;

Q: the pistons work end face, refer to piston or piston cover plate that working surface towards valve seat or cylinder head, can abbreviate top work surface as;

M: secure fit face M refers to the secure fit junction surface of valve seat or cylinder head and cylinder;

A: the pistons work end face centre of form, when finger is in minimum volume when the volume of the active chamber of compressor, the joint of cylinder shaft axis O2 and pistons work end face Q, this joint allows to exist certain position error, as matching gap, manufacturing and assembly error, position degree deviation that various distortion caused;

L: the equivalent length of connecting rod, refer to the distance of pistons work end face centre of form A and crank pin axle center line O3, wherein A is referred to as the equivalent connecting rod to the vertical line of O3;

α: the compression stroke deflection angle of equivalent connecting rod and cylinder shaft axis O2, equate with the compression stroke deflection angle of piston with respect to cylinder, also be called the piston compression stroke deflection angle;

α _Max: the maximum deflection angle of piston compression stroke;

β: the suction stroke deflection angle of equivalent connecting rod and cylinder shaft axis O2, equate with the suction stroke deflection angle of piston with respect to cylinder, also be called piston suction stroke deflection angle;

β _Max: the maximum deflection angle of piston suction stroke;

SR: the spherical radius when the pistons work end face is sphere.

Embodiment

With specific embodiment the present invention is further described below: referring to Fig. 1-16:

Reciprocating-piston type oil-less air compressor, it comprises: cylinder 1, cylinder head 2, valve seat 3, piston 4, connecting rod 5, crank pin 6, bent axle 7 and crankcase 8, wherein said piston 4 is fastenedly connected with connecting rod 5 employings or piston 4 is integral production with connecting rod 5, be fitted with seal ring or the sealing cup 9 made of self-enrichment material on the piston 4, the stub end of connecting rod 5 is sleeved on rotationally on the described crank pin 6 and with the crankshaft rotating shaft axis O1 of crank pin 6 around bent axle 7 by bearing structure and rotates, it is interior and reciprocating along the direction of cylinder shaft axis O2 that piston 4 is placed in cylinder 1, obviously, because piston 4 and connecting rod 5 fastening being connected as a single entity, so piston 4 certainly exists the oscillating motion with respect to cylinder 1; Need to prove, connecting rod bottom-end bearing and crank pin 6 coaxial settings, its shaft axis is called crank pin axle center line O3 (allow exist certain because of manufacturing tolerances, matching gap and the caused coaxiality error of various distortion), piston 4 can be that one-piece piston also can be split type piston in addition, so-called split type piston is meant that piston 4 can assemble by some parts are fastening, constitute piston 4 on the piston only such as adopting the piston cover plate and by screw it being fastenedly connected, wherein seal ring or sealing cup 9 are pressed on the piston only by described piston cover plate; Obviously, constitute the active chamber (certainly participate in enclosing structure also include various valve blocks and valve block hole, intake and exhaust port or pore, various Sealings etc.) of compressor by the inner hole surface one common peripheral of pistons work end face Q, valve seat or cylinder head work bottom surface P and cylinder 1, when the volume of this active chamber is in the suction stroke that process when increasing is compressor, the process that is in when dwindling when the volume of this active chamber then is the compression stroke of compressor; Greatest feature of the present invention is that described cylinder 1 adopts bias structure, be that cylinder shaft axis O2 and described crankshaft rotating shaft axis O1 are non-intersect, in other words have non-vanishing cylinder offset amount e, and reciprocating-piston type oil-less air compressor of the prior art adopts perpendicular structural type of two axial lines that is zero offset air cylinder structure bar none; It must be noted that, seal ring or sealing cup 9 equipped on the piston 4 of the present invention adopt self-enrichment material to make, so-called self-enrichment material comprises teflon, filling teflon or the like is at the interior employed self-enrichment material of various existing reciprocating-piston type oil-less air compressor, therefore compressor does not consume lubricant oil basically, and can provide the high-quality pressurized air of oil-containing not substantially, regulation according to relevant criterion, compressor of the present invention belongs to the category of oil-free air compressor, but this does not also mean that oil-containing anything but, because used bearing contains certain lubricant oil or grease, the lubricant oil evaporation that still has minute quantity under the condition of high temperature leaks out, so allows to exist the lubricant oil of trace in the high-pressure air of compressor of the present invention output.

In order to set forth technical characterstic of the present invention better, introduce several relevant definition earlier below in conjunction with accompanying drawing:

1) about positive bias cylinder and negative bias cylinder: at compressor operating to the compression stroke process and radius of crankshaft during perpendicular to cylinder shaft axis O2, observe along crankshaft rotating shaft axis O1 direction, if cylinder shaft axis O2 and crank pin axle center line O3 are with the same side that is in crankshaft rotating shaft axis O1, then be referred to as positive bias cylinder (see figure 1), if cylinder shaft axis O2 and crank pin axle center line O3 divide the both sides that are listed in crankshaft rotating shaft axis O1, then be referred to as negative bias cylinder (see figure 2).

2) about the top dead center and the lower dead center of piston: so-called piston top dead center is meant as pistons work end face centre of form A and is in the piston position farthest time the from crankshaft rotating shaft axis O1, this moment, the volume in compressor operating chamber was in the minimum volume state, be in the conllinear state at top dead center pistons work end face centre of form A, crank pin axle center line O3 and crankshaft rotating shaft axis O1, see Fig. 3 (a); So-called piston lower dead center is meant as pistons work end face centre of form A and is in piston position when crankshaft rotating shaft axis O1 is nearest, this moment, the volume in compressor operating chamber was in the maximum volume state, also be in the conllinear state at lower dead center pistons work end face centre of form A, crank pin axle center line O3 and crankshaft rotating shaft axis O1, see Fig. 3 (c).

3) about the maximum deflection angle of suction stroke of maximum deflection angle of the compression stroke of piston and piston: the maximum angle α of piston 4 equivalent connecting rod and cylinder shaft axis O2 when compression stroke _Max, also be the compression stroke maximum deflection angle of piston 4 with respect to cylinder 1, see Fig. 3 (d); The maximum angle β of piston 4 equivalent connecting rod and cylinder shaft axis O2 when suction stroke _Max, also be the suction stroke maximum deflection angle of piston 4 with respect to gas 1, see Fig. 3 (b); Need to prove that the mark that Fig. 3 provides is the situation of some scope size cylinder offset amount e, when the numerical value of cylinder offset amount e simultaneously might maximum angle α _MaxAnd β _MaxAppear on the bottom dead center position.

4) about the normotopia cylinder, the loxosis cylinder, normotopia piston and loxosis piston: so-called normotopia cylinder is meant that main body composition plane among the secure fit face M of cylinder 1 and valve seat 3 or cylinder 1 and cylinder head 2 and cylinder shaft axis O2 are in plumbness and (allow to exist certain manufacturing, assembling and various distortion inaccuracy), so-called loxosis cylinder is meant that main body composition plane in the secure fit face of cylinder 1 and valve seat 3 or cylinder 1 and cylinder head 2 and cylinder shaft axis O2 are in heeling condition and (allow to exist certain manufacturing, assembling and various distortion inaccuracy), the aforementioned body composition plane is to refer to that valve seat 3 or cylinder head 2 (allow to lay various gasket seals with the main plane that is connected of the secure fit face M of cylinder 1, heat insulating mattress or adjustment pad), it can be a part or its extension of valve seat or cylinder head work bottom surface P; So-called normotopia piston is meant that piston 4 has so a kind of pose structure, when pistons work end face Q is plane or class plane, equivalent connecting rod and pistons work end face Q are in plumbness, otherwise equivalent connecting rod and pistons work end face Q are so-called loxosis piston when being in the out of plumb state, here said plane or class plane general reference are based on the plane and contain some other curved surface such as chamferings, fillet, the fastening screw trip bolt counterbore, the air valve hole, various defective pitted surfaces and crowning, certain described plane also allows to exist certain manufacturing, assembling and the caused morpheme sum of errors of various distortion size error.

For the positive bias cylinder, when cylinder offset amount e is less than or equal to radius of crankshaft r (referring to Fig. 1 and Fig. 3), derive piston maximum compression stroke deflection angle α easily _MaxWith piston maximum inhale stroke deflection angle β _MaxBe respectively:

${\mathrm{\α}}_{\max }=\max \{\arcsin \left(\frac{r-e}{L}\right),\arcsin \left(\frac{e}{L-r}\right)\}$

${\mathrm{\β}}_{\max }=\max \{\arcsin \left(\frac{r+e}{L}\right),\arcsin \left(\frac{e}{L-r}\right)\}$

Notice the reciprocating-piston type oil-less air compressor of traditional reciprocating-piston type oil-less air compressor that is zero offset cylinder, under the base dimension r prerequisite equal with L, its piston maximum compression stroke deflection angle α _MaxWith piston maximum inhale stroke deflection angle β _MaxFor:

${\mathrm{\α}}_{\max }={\mathrm{\β}}_{\max }=\arcsin \left(\frac{r}{L}\right)$

Undoubtedly, when cylinder offset amount e is less than or equal to radius of crankshaft r, the maximum deflection angle of the piston compression stroke of positive bias cylinder reciprocating-piston type oil-less air compressor of the present invention can be done forr a short time than of the prior art, in other words the motion of the piston 4 of positive bias cylinder compressor approaches straight reciprocating motion more, obviously this is very favourable for the side pressure that reduces 4 pairs of cylinders 1 of piston, not only can reduce the wear extent of seal ring or sealing cup 9 thus, but also can reduce the intensity of bouncing of 4 pairs of cylinders 1 of piston, further can also reduce seal ring or the sealing cup 9 ovalizing deflection amplitude in the swing process of compression stroke, both can strengthen the ability of its antifatigue thus but also can reduce the leakage rate of pressurized gas, so the present invention adopts the positive bias cylinder can improve the operating life of compressor by oval slit, reduce the mechanical beat noise of compressor and reduce the pressurized gas ease noise that screams when escaping; Certainly, the maximum deflection angle of the piston suction stroke of positive bias cylinder reciprocating-piston type oil-less air compressor of the present invention is bigger than of the prior art, but the pressure when noticing suction stroke in the active chamber of compressor is very little, therefore the side pressure that produces is also little, what seal ring or sealing cup 9 were subjected in addition is intake negative-pressure, therefore its ovalizing deflection amplitude is little, and is apparent, and the negative effect that the positive bias cylinder produces in the suction stroke process is also not serious.

For the negative bias cylinder, when cylinder offset amount e is less than or equal to radius of crankshaft (referring to Fig. 2), derive piston maximum compression stroke deflection angle α easily _MaxWith piston maximum inhale stroke deflection angle β _MaxBe respectively:

${\mathrm{\α}}_{\max }=\max \{\arcsin \left(\frac{r+e}{L}\right),\arcsin \left(\frac{e}{L-r}\right)\}$

${\mathrm{\β}}_{\max }=\max \{\arcsin \left(\frac{r-e}{L}\right),\arcsin \left(\frac{e}{L-r}\right)\}$

The crankshaft rotating angle that this moment, piston 4 was finished a compression stroke correspondence is:

$\mathrm{\π}+\arcsin \left(\frac{e}{L+r}\right)-\arcsin \left(\frac{e}{L-r}\right)$

Clearly, the maximum deflection angle α of piston compression stroke _MaxBigger than the maximum deflection angle of the piston compression stroke of prior art, this is no doubt unfavorable to the wear condition of seal ring or sealing cup 9, but based on the compressor of pursuing Design of Low Noise, still be beneficial to for those, this is because the negative bias air cylinder structure can reduce the pairing crankshaft rotating angle of compressor compresses stroke, in other words the compression speed of shortening of compression stroke time corresponding or piston 4 accelerates, can reduce the time of gas leakage thus, the formed throttle effect of piston 4 motion quickenings also helps reducing leakage rate in addition, can remedy thus because of piston 4 swing angles increase the leakage loss produces, so also can reduce escape the noise that screams when escaping of the pressurized gas of compressor.

Need to prove, cylinder offset amount e also can be greater than radius of crankshaft r, this situation still has certain positive effect, but its positive effect of increase along with cylinder offset amount e is diminishing, and its negative effect is increasing, therefore cylinder offset amount e only is fit to be applied in the occasion that some has specific (special) requirements greater than the situation of radius of crankshaft r, just can consider such as wanting the very compact compressor of cube, because at this moment crank pin 6 can be dodged out piston 4 easily even be dodged out cylinder 1, possesses the condition of compact design.

Reciprocating-piston type oil-less air compressor of the present invention both can adopt the single cylinder form also can adopt the multi-cylinder form, cylinder 1 when adopting the single cylinder form, cylinder head 2, the quantity of piston 4 and connecting rod 5 is one (as Fig. 6 and shown in Figure 9), this moment, cylinder 1 can be that horizontal layout also can be that vertical layout can also be the oblique installing type layout, the cylinder shaft axis O2 that is cylinder 1 can be a level, various ways such as vertical and inclination, and cylinder 1 when adopting the multi-cylinder form, cylinder head 2, piston 4, the quantity of connecting rod 5 and accessory all can have a plurality of, multi-cylinder engine is the best to adopt two-cylinder version, this moment cylinder 1, cylinder head 2, the quantity of piston 4 and connecting rod 5 is two, the form of two cylinder machines can adopt cylinder in V-arrangement layout (as shown in Figure 4) and opposed cylinder layout (not shown), for the direct-coupled electrical machinery compressor driven even can also adopt two cover cylinders are split structural type at motor two; Adopt the benefit of multi cylinder to be, can adopt lower rotating speed at the prerequisite lower compression machine of same displacement, same cylinder size and piston stroke, all very favourable to reducing mechanical noise, induction noise and exhaust sound like this.

The crankcase 8 of reciprocating-piston type oil-less air compressor of the present invention can adopt open crankcase structure (as Fig. 5, Fig. 6 and shown in Figure 7), open crankcase is the structural type that present reciprocating type oil-free air compressor adopts, and is characterized in that piston 4, connecting rod 5, crank pin 6 and the bent axle 7 of compressor is in the exposed or half-naked state that reveals; In order to reduce the outside radiation magnitude of the mechanical noise that movement parts produces, simultaneously also in order to reduce the noise that screams that compression process mesohigh gas escapes to be produced by oval slot leakage ease to extraradial magnitude, crankcase 8 also can adopt enclosed crankcase structure (as Fig. 8, Fig. 9 and shown in Figure 10), the characteristics of closed crankcase are that crankcase 8 (allows to exist certain sealing off gap for enclosed structure, movement parts matching gap and various necessity be connected the ditch circulation passage), it can adopt crankcase cover 11 and various sealing gasket or seal ring to seal crankcase 8, the piston 4 of compressor like this, connecting rod 5, crank pin 6 and bent axle 7 will no longer present the exposed to external world or half-naked state that reveals, therefore the sound that screams that the mechanical noise of above-mentioned movement parts and gas ease is escaped will effectively be masked, and need to prove that crankcase cover 11 can be that a complete big member also can be made up of some little independently members; In addition, also need to prove, no matter be to adopt open crankcase structure or closed crankcase structure, the intake method of compressor and air inlet path all can be similar with prior art, such as compressor when carrying out suction stroke, fresh air is introduced into spatial transition in the cylinder head 2 through empty filter 10, and then via being opened in the suction port 15a on the valve seat 3 and pushing open in the active chamber that breather cheek valve 15b enters compressor, certainly, if cylinder head 2 directly also can directly be opened in suction port 15a on the cylinder head 2 in the face of pistons work end face Q.

When reciprocating-piston type oil-less air compressor of the present invention adopts closed crankcase structure, in order to reduce induction noise better, crankcase intake noise reduction chamber 12 can be made in those spaces by the relative closure of crankcase 8, crankcase cover 11, cylinder 1, piston 4 and some other associated components such as Sealing, bearing or the like one common peripheral structure, what described crankcase intake noise reduction chamber 12 allowed to exist certain sealing off gap, movement parts matching gap and various necessity is connected ditch circulation passage etc.; Need to prove, crankcase intake noise reduction chamber 12 can be connected with ambient atmosphere by suction port 13, suction port 13 both can be located at (as Fig. 8 and shown in Figure 10) on the crankcase cover 11 can be arranged on also that (as Figure 11 and shown in Figure 12) can also all be provided with simultaneously on the casing of crankcase 8 on the casing of crankcase cover 11 and crankcase 8, suction port 13 both can external air-strainer 10 also can not external air-strainer, both can be that the monotrysian type structure also can be that open grain structure can also be plane-of-weakness joint type or cellular structure, in addition, crankcase intake noise reduction chamber 12 also communicates with the active chamber of compressor, it can be by passing through suction port 15a behind the spatial transition in the air pipe 14 connection cylinder head 2 again, the active chamber of breather cheek valve 15b and compressor is linked up (as Fig. 9 and shown in Figure 10), certainly suction port 15a and breather cheek valve 15b can be installed in (as Figure 11 and shown in Figure 12) on the piston 4, and the air inlet path of this moment is more convenient; Be not difficult to find, in the process that suction stroke is carried out, the volume of crankcase intake noise reduction chamber 12 is subjected to the compression of piston 4 and diminishes, undoubtedly will be regurgitated from suction port 13 parts again by some air that has entered in the crankcase intake noise reduction chamber 12, thereby cause the air inlet of pulsating nature to regurgitate noise, and among the noise that screams that pressurized gas produce when escaping by oval slot leakage ease also can radiate outwardly to extraneous atmosphere from this suction port 13, the present invention prevents by the gas-entered passageway 13b that breather check valve 13a or setting are set have certain-length and space or alleviates this phenomenon for this reason, wherein the end of gas-entered passageway 13b is air outlet 13c, described air outlet 13c is connected with crankcase intake noise reduction chamber 12, the other end of gas-entered passageway 13b then is connected with suction port 13, described breather check valve 13a can be arranged on suction port 13 places (as shown in figure 11), also can be arranged on the 13c place, air outlet of gas-entered passageway 13b, certainly can also be arranged on this place, two places (as shown in figure 12) simultaneously, in addition can also be within gas-entered passageway 13b some various muffler materials used in the prior art and filtering materials of filling, comprise foam, sponge, cotton-wool, the cloth wadding, various fibers, wire or refill or the like, it is worthy of note, gas-entered passageway 13b can make a long channel and also can be made of some expansion chambers that are interconnected, and undoubtedly can solve scream noise and the air inlet that produce when pressurized gas are escaped by oval slot leakage ease well by above-mentioned measure and regurgitate noise.

The present invention is because adopt the organization plan of offset cylinder, therefore might change the compression exhaust process of compressor, such as when adopting negative bias air cylinder structure scheme or when adopting cylinder offset amount e greater than radius of crankshaft r, the time that compression stroke spent of compressor will lack with respect to the time that suction stroke spent, the pulsatile impact that the pressurized gas that this moment, pressurized gas was discharged via exhaust port 16a and exhaust check valve 16b produce may become violent, the mechanical impact noise that sends in order to reduce the exhaust check valve 16b that causes thus to impact valve seat 3, tighten at valve seat 3 especially and be connected with exhausting silencer cover 17a (as Figure 11 and shown in Figure 12), described exhausting silencer cover 17a with exhaust check valve 16b shroud within it, and formation exhausting silencer chamber 17b, described exhausting silencer chamber 17b is communicated with the exhaust transition chamber of cylinder head 2 within cylinder head 2 and by through hole 17c by shroud, wherein can be one also can be a plurality of to the quantity of through hole 17c, can be circular hole or flat hole or other irregularly-shaped holes, can be opened in and also can be opened on valve seat 3 or the cylinder head 2 on the exhausting silencer cover 17a, can constitute two-stage and even multistage expansion noise elimination structure by exhausting silencer chamber 17b and exhaust transition chamber, so can reduce exhaust sound, what is more important exhausting silencer cover 17a has carried out the interception of shielding with those from the pulse feature pressurized gas that relief opening 16a goes out, impact thereby avoid its body to produce directly, so can effectively reduce the exhaust impact noise cylinder head 2.

Reciprocating-piston type oil-less air compressor of the present invention can have the combination of cylinder 1 with the piston 4 of multiple structural type: first kind of combination is to adopt the normotopia cylinder to join loxosis piston (as shown in figure 13), second kind of combination is to adopt the loxosis cylinder to join normotopia piston (as shown in figure 14), the third combination is to adopt the loxosis cylinder to join loxosis piston (as shown in figure 15), and the 4th kind of combination is to adopt ball top cylinder to join spherical-head piston (as shown in figure 16); Need to prove, so-called ball top cylinder and spherical-head piston are meant that the top work surface Q of piston 4 is a spherical structure, correspondingly the work bottom surface P of valve seat or cylinder head also is spherical structure, wherein spherical structure does not require and must adopt complete sphere, allow between them to have certain clearance in case when top dead center, clash into, the spherical radius SR of spherical-head piston cylinder pore radius best and cylinder matches, adopting the benefit of spherical structure is the oval slit that can eliminate preferably between piston 4 and the cylinder 1, the gas noise that screams that can reduce leakage and cause because of leakage.

The purposes of reciprocating-piston type oil-less air compressor can be used for making air compressor or gas pump or vacuum pump or fluid pump.

The foregoing description only is several preferred embodiments of the present invention, and is not to limit protection scope of the present invention according to this, so: all various equivalences of doing according to structure of the present invention, shape, principle change, and all should be covered by within protection scope of the present invention.

Claims (13)

1. reciprocating-piston type oil-less air compressor, it comprises: cylinder, piston, connecting rod, bent axle and crankcase, the other end that one end of described cylinder is connected with cylinder head or valve seat, cylinder is connected with crankcase, described piston and connecting rod adopt and are fastenedly connected or piston and connecting rod are integral production, piston is positioned in the cylinder and the reciprocating and oscillating motion with respect to cylinder, it is characterized in that: the crankshaft rotating shaft axis of described bent axle has an offset distance at a distance of the cylinder shaft axis of cylinder, forms positive bias air cylinder structure or negative bias air cylinder structure.

2. reciprocating-piston type oil-less air compressor according to claim 1 is characterized in that: described cylinder, piston, connecting rod and accessory respectively have one or more.

3. reciprocating-piston type oil-less air compressor according to claim 2 is characterized in that: described piston is split type piston or is one-piece piston.

4. reciprocating-piston type oil-less air compressor according to claim 3 is characterized in that: described crankcase is closed crankcase structure.

5. reciprocating-piston type oil-less air compressor according to claim 4 is characterized in that: described crankcase constitutes crankcase intake noise reduction chamber.

6. reciprocating-piston type oil-less air compressor according to claim 5 is characterized in that: described crankcase intake noise reduction chamber is connected with ambient atmosphere by suction port; Perhaps crankcase intake noise reduction chamber is connected with ambient atmosphere by gas-entered passageway and suction port.

7. reciprocating-piston type oil-less air compressor according to claim 6 is characterized in that: the place is provided with breather check valve at described suction port; Perhaps be provided with one-way valve at the place, air outlet of gas-entered passageway; Perhaps in gas-entered passageway, be provided with muffler material or filtering material.

8. according to each described reciprocating-piston type oil-less air compressor in the claim 1 to 7, it is characterized in that: the crankshaft rotating shaft axis of described bent axle is less than or equal to the turning radius of bent axle with respect to the offset distance of the cylinder shaft axis of cylinder.

9. according to each described reciprocating-piston type oil-less air compressor in the claim 1 to 7, it is characterized in that: described valve seat or cylinder head are provided with the exhausting silencer cover.

10. according to each described reciprocating-piston type oil-less air compressor in the claim 1 to 7, it is characterized in that: the work bottom surface of the top work surface of described piston, valve seat or cylinder is plane or class plane.

11. according to each described reciprocating-piston type oil-less air compressor in the claim 1 to 7, it is characterized in that: described cylinder is that normotopia cylinder and piston are the loxosis piston; Perhaps described cylinder is that loxosis cylinder and piston are the normotopia piston; Perhaps described cylinder is that loxosis cylinder and piston are the loxosis piston.

12. according to each described reciprocating-piston type oil-less air compressor in the claim 1 to 7, it is characterized in that: the work bottom surface of the top work surface of described piston, valve seat or cylinder is sphere.

13. the purposes of reciprocating-piston type oil-less air compressor can be used for making air compressor or gas pump or vacuum pump or fluid pump.

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