CN1107793C - Double moving piston type compressor - Google Patents

Abstract

To provide a double acting piston type compressor to be used for supercharging of, for example, an internal combustion engine. This double acting compressor comprises a pump cylinder body 20 having two ends closed by a first and second pump cylinder heads 231 and 232 ; and a pump piston 25 provided at two ends and between the first and second pump cylinder heads 231 and 232 with a first and second piston heads 251 and 252 to partition a first and second pump chambers 361 and 362 from each other. A pump crank shaft 26 and a connecting rod 40 to connect the pump crank shaft to a pump piston 25 are disposed in a working chamber 37 arranged in the pump piston 25, and through rotation of the pump crank shaft 26, the pump piston 25 is forced to effect reciprocation.

Description

Double moving piston type compressor

Technical field

The present invention relates to a kind of compressor that boosts to explosive motor that for example is used to, particularly relate to a kind of to-and-fro motion that utilizes pump piston, the suction of the gas that carries out and the double moving piston type compressor of discharge.

Background technique

In the past, for boosting to explosive motor, the pump piston of the single pump chamber that forms in bent axle and the pumping cylinder is connected, to-and-fro motion according to this pump piston, make it carry out the single-linkage piston type compressor of pumping action in above-mentioned pump chamber, this compressor is disclosed on the communique of the public clear 55-27218 of known spy.

In aforesaid single-linkage piston type compressor, the pump piston to-and-fro motion is once had to pumping action one time, so the piston size of per unit discharge capacity is big, the miniaturization of compressor is difficult.

Summary of the invention

The present invention finishes in view of the foregoing, and its purpose is to provide the pump piston size of a kind of unit average discharge little, compact, and the good double moving piston type compressor of endurance.

For achieving the above object, a kind of double moving piston type compressor of the present invention, be provided with pump cylinder main body and pump piston, wherein the pump cylinder main body contains the cylinder-bore that two ends are closed by the 1st and the 2nd pumping cylinder lid, and pump piston is provided with the 1st and the 2nd piston termination at two ends, be divided into the 1st and the 2nd pump chamber separately respectively and be entrenched on the cylinder-bore with being free to slide between itself and the 1st and the 2nd pumping cylinder cover; It is characterized in that: on this pump piston, form the working room that connects two piston terminations, the crankpin and the connecting rod of pump crankcase is set in this working room, this pump crankcase is connected with rotary driving source; Bearing part freedom on the clutch shaft bearing hole that this connecting rod forms by an end that is contained in connecting rod joltily is connected on this crankpin, simultaneously, the bearing part of the 2nd bearing hole that forms by the other end that is contained in connecting rod joltily is connected on the wrist pin of pump piston place setting with the piston freedom, rotation forcing pump reciprocating motion of the pistons by the pump crankcase pin, and, on connecting rod, form the accumulator of the lubricant oil of packing into, simultaneously, this accumulator is communicated with the 1st and the 2nd bearing hole.

According to this feature, single pump piston makes the first and second pump chamber work, can increase the comprehensive air displacement of gas, and therefore, the size of the pump piston each several part of every comprehensive unit air displacement can be dwindled.Also have, owing to adopt connecting rod, in the rotation of pump cylinder axis, the variation of the speed of shaking of the connecting rod corresponding with wrist pin is always level and smooth, can improve the durability of the connecting rod bearing bearing of supporting piston.

According to this feature, each needle bearing all is a minor diameter, and load capacity is big, therefore can improve the mutual join strength of connecting rod and crankpin and wrist pin, can fully improve the patience when running up.

According to eigen, along with shaking of connecting rod, the lubricant oil of accumulator, because of reciprocating inertial force effect to separately accumulator supplying lubricating oil, effectively lubricating needle bearing separately better naturally.

The present invention also has following the 2nd feature outside above-mentioned feature, be provided with following valve at each pumping cylinder lid: open when each pump chamber decompression and make each pump chamber suck the suction valve of gas, and each pump chamber is opened the expulsion valve of discharging gas from each pump chamber when boosting.

According to this feature, the installation of suction valve and expulsion valve can become easily, and can help the further miniaturization of compressor.

In addition, the present invention also has following the 3rd feature on first feature, on first and second bearing hole, each bearing part of clamping is installed, seals the 1st and the 2nd sealed member of this bearing hole.

In addition, the present invention also has the 4th feature on the 1-3 feature: described bearing part is a needle bearing.

According to this feature, can prevent to flow out lubricant oil constantly lubricated effectively each needle bearing from each bearing hole.

The present invention also has the 5th feature on the 1-4 feature in addition, is unkitted piston ring in the described pump piston.

The present invention on first feature, also has the 6th feature, by pump subject freedom supporting crankshaft rotatably.

According to this feature, pump crankcase can be supported securely by the pump cylinder main body of high rigidity.

Description of drawings

Fig. 1 is the automatic two-wheel vehicle used explosive motor longitudinal plane profile that is provided with double moving piston type compressor of the present invention.

Fig. 2 is the sectional view along the 2-2 line of Fig. 1.

Fig. 3 is the sectional view along the 3-3 line of Fig. 1.

Fig. 4 is the longitudinal plane profile that the double moving piston type compressor among Fig. 1 enlarges.

Fig. 5 is the sectional view along the 5-5 line of Fig. 4.

Fig. 6 is the sectional view along the 6-6 line of Fig. 5.

Fig. 7 is the view along the arrow of Fig. 4.

Fig. 8 is an above-mentioned compressor major component plane exploded view.

Fig. 9 is an above-mentioned compressor major component longitudinal plane exploded view.

Figure 10 is the line chart that shows the pump piston work schedule of the switching sequence of suction valve, expulsion valve and back-up valve of above-mentioned explosive motor and above-mentioned compressor.

Figure 11 is the line chart that shows the needle bearing running speed variation of pump piston side in the above-mentioned compressor.

Figure 12 shows near the modified example sectional view the relief valve in the above-mentioned compressor.

Embodiment

To form of the invention process,, carry out following explanation with reference to the embodiment of the invention shown in the accompanying drawing.

In Fig. 1 to Fig. 3, symbol E represents to have the automatic two-wheel vehicle used explosive motor of double moving piston type compressor C of the present invention.The engine main body 1 of this explosive motor E, constitute by with bolt cylinder cap 1b being connected by upper-end surface at cylinder body 1a, at this cylinder cap 1b, formed near the firing chamber 3 of the termination of the piston 2 that is contained in cylinder body 1a and intakeport 4, the relief opening 5 and the mouth 6 that boosts that link to each other respectively with this firing chamber 3.At cylinder cap 1b, suction valve 7, expulsion valve 8, the back-up valve 9 that opens and closes intakeport 4, relief opening 5 and overvoltage mouth 6 respectively has been installed and lighted the ignition plug 10 of the mixed gas that imports firing chamber 3, open and close a valve cam axle 11 of above-mentioned three valves 7,8,9; At this moment back-up valve 9 and ignition plug 10 become the V font to arrange with the axial direction of valve cam axle 11, and suction valve 7 is becoming the direction of craspedodrome to become V-shape arrangement, configuration respectively with expulsion valve 8 with the axial direction of camshaft 11.Each valve 7,8,9 has all been installed the valve spring 12,13,14 that suppresses towards closing direction.

Valve cam axle 11 by pairing left and right ball bearing 16,15, is supported in cylinder cap 1b, has disposed air-breathing cam 11i of using and exhaust cam 11e between above-mentioned two bearings 15,16, the protruding terminus outside right-hand bearing 16, and having disposed boosts uses cam 11c.And the protruding terminus in bearing 15 outsides of the left of this valve cam axle 11 be fixed with that the crankshaft (not shown) that is connected with piston 2 by chain 17 drives by movable sprocket 18.Air-breathing and exhaust is used cam 11i, 11e by rocker arm 19i, 19e air-breathing and that exhaust is used, engage with suction valve 7 and expulsion valve 8, boost that it is tapered to do with cam 11c, directly engage with back-up valve 9.

Thereby, if pass through chain 17 by no illustrated bent axle, actuating valve camshaft 11 is then because the association of air-breathing, exhaust and boost cam 11i, 11e, 11c and valve spring 12,13,14 action usefulness just can open and close suction valve, expulsion valve and back-up valve 7,8,9 respectively according to sequential shown in Figure 10.

Aforementioned intakeport 4 and relief opening 5, as explosive motor, be communicated with air-breathing menifold and discharge manifold (all not having diagram), boost mouthfuls 6 with abut against the discharge conduit 57 that boosts with the double acting piston formula air compressor C of the present invention of cam 11c outer end and be communicated with.

In Fig. 4, Fig. 5 and Fig. 7, double moving piston type compressor C has following setting: the pump cylinder main body 20 about bearing spider head 21,22 is protruded on two outer side surfaces, be free to slide the chimeric pump piston 25 in ground with cylinder-bore 24 at this pump cylinder main body 20, and the pump crankcase 26 that drives this pump piston 25.This pump cylinder main body 20 is chimeric with the mounting hole 27 of aforementioned cylinder cap 1b right side wall with the bearing spider termination 21 (referring to Fig. 7) of left, is connected by bolt 28.

Pump piston 25 is not set up piston ring, can directly slide in the cylinder-bore 24 of pump cylinder main body 20, scribbles the lubricating grease of lubricated usefulness on these slip surfaces.

At bearing spider head 21,22 places, the bearing spider hole 21a, the 22a that arrive pump cylinder main body 20 the insides are arranged, in bearing spider hole 21a, 22a, ball bearing 29,30 is installed, is supporting pump crankcase 26, simultaneously the other end of pump crankcase 26, by spline 31, combine with aforementioned valve cam axle 11.And the bearing hole 21a of left in bearing 29 outsides, is installed with the oil sealing 32 that closely links to each other with pump crankcase 26 peripheries.This oil sealing 32 has adopted the high pressure type that can bear the described relief valve 75 cracking pressure degree in back.

At right-hand bearing spider hole 21a sealing plug 33 with the outer side surface adjacency of bearing 30 is installed, what cover sealing plug 33 simultaneously emits 34, is used the outside of screw threads for fastening at bearing spider head 22.

The two ends in the cylinder hole 24 of pump cylinder main body 20 are by first and second paired pumping cylinder lid 23 ₁, 23 ₂Sealing is at itself and cylinder cap 23 ₁And 23 ₂Between be distinguished into first and second pump chamber 36 ₁, 36 ₂First and second piston head 25 ₁, 25 ₂, be formed at the two ends of pump piston 25.

At pump piston 25 places, be formed with to first piston termination 25 ₂Two piston terminations 25 are moved and connected to lateral deviation ₁, 25 ₂Circular working room 37 and lateral direction penetrating first piston termination 25 ₁And the piston pin hole 38 of supporting piston pin 39, in this working room 37, holding the crankpin 26a of pump crankcase 26 and this crankpin 26a is being connected the connecting rod 40 of wrist pin 39.

Connecting rod 40, clutch shaft bearing hole 40a is arranged in the end of crankpin 26a side, the second bearing hole 40b is arranged in the end of wrist pin 39 sides, first and second needle bearing 41,42 that install at these bearing holes 40a, 40b place is supporting above-mentioned crankpin 26a and wrist pin 39 respectively.And at 40a place, clutch shaft bearing hole, clip first needle bearing 41, the pairing left and right sealed member 43,43 that connects airtight with crankpin 26a periphery has been installed,, has been clipped second needle bearing 42 the pairing left and right sealed member 44,44 that connects airtight with wrist pin 39 peripheries has been installed at the second bearing axis hole 40b.

Be formed with therebetween part by the airtight accumulator 46 of cap 45 at connecting rod 40, the oilhole 47,48 that is communicated with two bearing hole 40a, 40b respectively simultaneously passes this accumulator 46, is packaged with the lubricating grease that lubricates usefulness in the accumulator 46.

Pump piston 25 for easy processing, between aforementioned working room 37 and aforementioned piston pin hole 38, is divided into two piston halfbody 25a, 25b, and these two piston halfbody 25a, 25b are connected by a plurality of bolts 49.

To shown in Figure 6, cover 23 as Fig. 4 at first and second pumping cylinder ₁, 23 ₂On the opposite of itself and pump cylinder main body 20, be provided with embedding hole 50 respectively, than this embedding hole diameter circlet shape exhaust chamber 51 and the columnar induction chamber 52 that centered on by this exhaust chamber 51, under the state that these embedding holes 50 is entrenched in the two ends outside of pump cylinder main body 20, with several through hole bolts 53 and nut 54 with two pumping cylinders lids 23 ₁, 23 ₂Mutually combine and be one.

And at two pumping cylinder lids 23 ₁, 23 ₂On, first connecting tube 55 that is communicated with between the suction chamber 52,52 has been installed ₁And be communicated with second connecting tube 55 of 51,51 of exhaust chambers ₂, particularly at second pumping cylinder lid 23 ₂Be connected with at the suction lead 56 that does not have this induction chamber 52 that illustrated air-breathing menifold intermediate portion is communicated with of explosive motor E with at explosive motor E mouthfuls 6 exhaust manifolds 57 that are communicated with these exhaust chambers 51 that boost.

Pump cylinder main body 20 reaches pumping cylinder lid 23 separately ₁, 23 ₂Between on embedding hole 50, control valve unit 58 is by following setting.

That is, as Fig. 8 and shown in Figure 9, valving 58 by ring-type backboard 60, thin-walled suck valve plate 61, seat board 62, and thin-walled shape discharge valve plate 63 and overlap successively.These component parts 60,61,62,63, it has the circle of roughly the same external diameter in the end that forms with pump cylinder main body 20 of periphery separately.And this control valve unit 58 is entrenched in corresponding pump cylinder main body end 23 together in the end that the end face side of pump cylinder main body 20 has disposed backboard 60 and this pump cylinder main body 20 ₁, 23 ₂Embedding hole 50 in, be clipped in pump cylinder main body 20 and each pumping cylinder the lid 23 ₁, 23 ₂Between.This clamping force on one side by through bolt 53 and nut 54 clamping pump cylinder main bodies 20, has been utilized first and second pumping cylinder lid 23 on one side as previously mentioned ₁, 23 ₂The combination force that combines.

At this moment, first locating stud 65 ₁Be entrenched in and be located at pumping cylinder lid 23 ₁, 23 ₂, first positioning hole 64 of discharging valve plate 63 and on seat board 62, being provided with ₁, while second locating stud 65 ₂Be entrenched in and be located at valve seat 62, suck valve plate 61, and second positioning hole 64 of backboard 60 ₂

On seat board 62, four groups of ternary inlet holes 67, around 90 degree are arranged in its central position, and, near its periphery, be equipped with two groups seven one group exhaust port 68, become 180 degree to arrange at interval.

Sucking valve plate 61, be provided with four the inhalation reed valve 61as corresponding with above-mentioned four groups of inlet holes 67, and not inaccessible for making around its two circular arc slotted holes 69 establishing with above-mentioned two groups of exhaust ports 68.Each inhalation reed valve 61a, close to the periphery that sucks valve plate 61 as possible for making the bottom, the top is close to the center that sucks valve plate 61 as possible, and it is extended to the radial direction that sucks valve plate 61, by around it, forms sucking valve plate 61 upper cuts.

The interior week of backboard 60 is provided with the breach shape limitation part 60a corresponding with the bottom of above-mentioned each inhalation reed valve 61a, has been stipulated the deflection fulcrum of inhalation reed valve 61a by this limitation part 60a.So in a single day, form breach shape limitation part 61a, not influenced by cylinder-bore 24 edge of opening of pump cylinder main body 20, make the bending length lengthening that sucks guiding reed 61a as far as possible.As long as if it is just passable to make when wanting to allow this bending length shorten limitation part 60a form convex.

Discharge valve plate 63, be provided with two the exhaust reed valve 63as corresponding and for not stopping up the large-diameter circular hole 70 that above-mentioned four groups of inlet holes 67 surround it with above-mentioned two groups of exhaust ports 68.Exhaust reed valve 63a forms at exhaustion plate 63 otch on every side along it.

And on seat board 62, connect above-mentioned circular hole 70, form and corresponding cylinder cap 23 ₁, 23 ₂The chimeric ring bulkhead 62a of suction chamber 52 inner peripheral surfaces, separate suction chamber 52 and exhaust chamber 51 thus.

As shown in Figure 5, at the sidewall of pump cylinder main body 20, be provided with the valve mounting hole 71 in its outer openings, and connect the overflow hole 72 of these valve mounting hole 71 diapires, the annular groove 77 that this overflow hole is communicated with aforementioned working room 37 is formed at the inner peripheral surface of pump cylinder 20.Valve gap 73 and aforementioned first connecting tube 55 ₁Periphery airtight chimeric, in first connecting tube 55 ₁The interior through hole 74 that is communicated with valve gap 73, break-through is provided with a plurality of on the perisporium of first connecting tube 55.The valve spring 76 that has held the relief valve 75 that can open and close above-mentioned overflow hole 72 and utilized the design (calculated) load of regulation to suppress at valve gap 73 to closing direction.

In addition, in Fig. 4, symbol 80 is provided in a side of each pumping cylinder lid 23 ₁, 23 ₂The peep hole of last arrival suction chamber 52 is usually by bolt 81 lockings.

The following describes effect about present embodiment.

E is in service at explosive motor, and the pump crankcase 26 of compressor C is driven by operating valve camshaft 11, by connecting rod 40, makes pump piston 25 to-and-fro motion forcibly, follows this motion, at first and second pump chamber 36 ₁, 36 ₂Repeat decompression, pressurization alternately.

At first pump chamber 36 ₁During decompression, according to the unlatching of the inlet hole 67 of the locking of the exhaust port 68 of exhaust reed valve 63a and inhalation reed valve 61a, the air in the no illustrated air-breathing menifold of explosive motor E from suction lead 56 orders through first connecting tube 55 ₁, suction chamber 52, inlet hole 67, be inhaled into this pump chamber 36 ₁And at this pump chamber 36 ₁During pressurization, according to making inlet hole 67 lockings owing to inhalation reed valve 61a and opening this pump chamber 36 owing to exhaust reed valve 63a makes exhaust port 68 ₁Forced air pass through exhaust chamber 51, second connecting tube 55 successively from exhaust chamber 68 ₂, exhaust manifolds 57 deliver to explosive motor E boost mouthfuls 6.

At second pump chamber 36 ₂During decompression, utilize and first pump chamber 36 ₁The unlatching of closing valve and inhalation reed valve 61 of the same exhaust reed valve 63a of situation, the air in the air-breathing menifold of explosive motor E is from suction lead 56, without first connecting tube 55 ₁, be inhaled into induction chamber 52, inlet hole 67, pump chamber 36 ₂And, this pump chamber 36 ₂During pressurization, utilize and first pump chamber 36 ₁The pass valve of the same inhalation reed valve 61a of situation and the unlatching of exhaust reed valve 63, this pump chamber 36 ₂Forced air, by exhaust port 68 to exhaust chamber 51 and without second connecting tube 55 ₂,, supply with explosive motor and boost mouthfuls 6 to exhaust manifolds 57 exhausts.

In addition in explosive motor E, suction valve 7, expulsion valve 8 and back-up valve 9 open and close by sequential shown in Figure 10, and particularly back-up valve 9, from the suction stroke to the compression stroke, just suction valve 7 will close preceding and close after certain hour in open valve.And when back-up valve 9 is closed, by aforesaid first and second pump chamber 36 ₁, 36 ₂The high-pressure air of supplying with at mouthful 6 pressure accumulations that boost, when back-up valve 9 is driven valve, that is, finishes to compression stroke from suction stroke, and mouth 6 is given the high-pressure air supercharging to firing chamber 3 from boosting.Consequently, can improve charging efficiency, give full play to the high output capability of explosive motor.

Therefore for compressor C, owing to make first and second pump chamber 36 by a pump piston 25 ₁, 36 ₂Interworking is so can realize the miniaturization of compressor C widely owing to the pump piston 25 each several part size decreases of the comprehensive average air displacement of unit.

And, pump crankcase 26, owing to be to support by a pair of ball bearing on the two side of pump cylinder main body 20 29,30, so can support pump crankcase 26 securely by the pump cylinder main body 20 of high rigidity.

And pump piston 25, owing to drive by pump crankcase 26 by connecting rod 40, and in the rotation of pump crankcase 26, the velocity variations of shaking of wrist pin 39 connecting rods 40 is very level and smooth relatively, therefore, as shown in figure 11, the variation of the rotational speed of the needle bearing 42 of supporting piston pin 39 also usually becomes smoothly, can improve its durability.

And pump piston 25 is because directly slip the cylinder-bore 24 of the pump cylinder main body 20 that piston ring is not set in, so that the power loss that is caused by its slip resistance can suppress is very little.But owing to there are not piston ring, each pump chamber 36 ₁, 36 ₂High-pressure air leak unavoidably to working room 37 by the micro-gaps in pump piston 25 and the cylinder-bore 24, be not so good as like this by utilizing this leakage to be boosted in working room 37, thereby make first and second pump chamber 36 ₁, 36 ₂The pressure difference of pressure during pressurization and working room 37 reduces.Its result, the leakage rate to working room 37 reduces, and can improve pump chamber 36 separately ₁, 36 ₂Working efficiency.

37 internal pressures rise when having surpassed the pressure of regulation in the working room, and relief valve 75 is opened, by pressure unnecessary in the working room 37 to the first lower connecting tube 55 of pressure ₁Therefore discharging has prevented excessively boosting of working room 37, can improve the durability of oil sealing 32 and other oil sealing bar, simultaneously, also can prevent by working room 37 to explosive motor E cylinder cap 1b gas leakage.And, because to first connecting tube 55 ₁The gas of discharging is once more to first and second pump chamber 36 ₁, 36 ₂Suction is entered, not to outside drain, and not waste.

In addition, first and second bearing spider hole 40a, the 40b at the two ends of connecting rod 40, respectively by first and second needle bearing 41,42 supporting crankshaft pin 26a and wrist pin 39, so even needle bearing 41,42 separately has its load capacity of less diameter also big, therefore, join strength height between pump crankcase 26 and the pump piston 25, and can abundant anti-high speed rotating.And, each bearing hole 40a, 40b are respectively by a pair of sealed member 43,43 and 44,44 sealing both ends, simultaneously, oilhole 47,48 by accumulator 46 places that form at connecting rod 40 intermediate portions is being communicated with, so when shaking along with the rotation connecting rod 40 of pump crankcase 26, the lubricating grease of accumulator 46 supplies to each bearing hole 40a, 40b naturally by action of centrifugal force, lubricated each needle bearing 41,42 o'clock more can improve its durability.

In addition, constitute backboard 60, suction valve plate 61, the seat board 62 of control valve unit 58, and discharge valve plate 63, because its periphery has all formed with pump cylinder main body 20 ends and had the circle of roughly the same external diameter,, these cover 23 so being entrenched in the pumping cylinder corresponding with pump cylinder main body 20 ends ₁, 23 ₂Embedding hole 50 in, can be clipped in pump cylinder main body 20 and the lid of pumping cylinder separately 23 ₁, 23 ₂Between.Therefore when can carrying out the assembling of control valve unit 58 easily, owing to cover 23 with pumping cylinder ₁, 23 ₂These are covered, so can protect and the contacting of other material.

This in addition situation is as the clamping force to control valve unit 58, owing to utilized through hole bolt 53 and 54 pairs of pump cylinder main bodies of nut 20 and first and second pumping cylinder lid 23 ₁, 23 ₂Combination force, so control valve unit 58 does not need special-purpose assembly, help the simplification of structure.And at pumping cylinder lid 23 separately ₁, 23 ₂, discharge first positioning hole 64 that valve plate 63 and seat board 62 are set up ₁Located first locating stud 65 chimeric ₁, second positioning hole 64 that the while sets up at seat board 62, suction valve plate 61 and backboard 60 places ₂Chimeric second locating stud 65 ₂So, when control valve unit 58 assemblings, can easily, positively keep each constituent material at pumping cylinder lid 23 ₁, 23 ₂The location of near axis, thereby prevent the mistake assembling of control valve unit 58, can guarantee the long-term normal valve work of valve.

Figure 12 shows other embodiment of the present invention, and right-hand ball bearing 30 is screwed tight sealing cover 34 at pump cylinder main body 20 right-hand bearing spider heads 22 ' directly pressing, this sealing cover 34 ' end wall on overflow hole 72 and valve mounting hole 71 are being set.In addition near sealing cover 34 ' first connecting tube 55 of configuration ₁, here the valve gap 73 of An Zhuaning is entrenched on the above-mentioned valve mounting hole 71.On this valve gap 73, relief valve 75 and valve spring 76 have equally been held with the example of aforementioned enforcement.In addition, on pump crankcase 26, be provided with working room's 37 connections at sealing cover 34 ' interior through hole 82.Other structure is because same previous embodiments, thus the part corresponding with former embodiment represent with prosign, and omitted these explanations.

Even and this embodiment, also the pressure that exceeds the quata of working room 37 can be discharged into first connecting tube 55 of low pressure from overflow hole 72 ₁In.

The invention is not restricted to the various embodiments described above, in the scope that does not break away from main idea of the present invention, can do all changes.For example, piston ring can be installed in the periphery of pump piston 25.

As above such, in accordance with a first feature of the invention, be provided with pump cylinder main body and piston termination, wherein there is the cylinder-bore of closing by first and second pumping cylinder lid at pump cylinder main body two ends; And pump piston two ends be provided with and first and second pumping cylinder lid between be divided into first and second piston termination of the 1 2nd pump chamber respectively, be entrenched on the pump cylinder-bore with being free to slide.On this pump piston, form the working room that connects between two piston terminations, be provided with the crankpin and the connecting rod of the pump crankcase that links to each other with rotary driving source in this working room, wherein, connecting rod one end shakes and is connected freely on this crankpin, and the other end freedom joltily is connected on the wrist pin that is provided with on the pump piston simultaneously; Because therefore the rotation forcing pump reciprocating motion of the pistons by pump crankcase, makes first and second pump chamber work by single pump piston, thereby, the comprehensive air displacement of gas is increased, so shorten pump piston each several part size, can seek the miniaturization of compressor.And owing to adopt connecting rod, in the pump crankcase rotation, the variation that the connecting rod of corresponding wrist pin shakes speed becomes usually smoothly, can improve the durability of bearing portion of the connecting rod of supporting piston pin.

In addition according to second feature of the present invention, be equipped with the pumping cylinder lid, open owing to being provided with the decompression of each pump chamber and gas is sucked open the expulsion valve that gas is discharged from each pump chamber when the suction valve of pump chamber separately and each pump chamber boost, therefore suction valve and expulsion valve can easily be installed, realize the microminiaturized more of compressor simultaneously.

And according to the 3rd feature of the present invention, because on the clutch shaft bearing hole that connecting rod one end forms, Jie is chimeric by the crankpin of needle bearing and pump crankcase, in addition on second bearing hole that the other end of connecting rod forms, Jie is chimeric by needle bearing and wrist pin, so needle bearing diameter separately is little, load capacity is big, thereby can improve the join strength between connecting rod and crankpin and the wrist pin, can abundant anti-high speed rotating.

And in addition according to the 4th feature of the present invention, on the 1st and the 2nd bearing hole, clip each needle bearing and seal the 1st and the 2nd sealed member in this bearing hole owing to having installed, thus can prevent to flow out lubricant oil from each bearing hole, can often lubricated effectively each needle bearing.

And in addition according to the 5th feature of the present invention, form the accumulator of enclosing lubricant oil at connecting rod, simultaneously owing to this accumulator is communicated with on the 1st and the 2nd bearing hole, so along with connecting rod shakes, the lubricant oil of accumulator is supplied to accumulator naturally by action of centrifugal force, can lubricate each needle bearing effectively.

And in addition according to the 6th feature of the present invention, owing to bent axle is supported on the pump cylinder main body with freely turning round, so can support pump crankcase securely by the pump cylinder main body of high rigidity.

Claims (7)

1. a double moving piston type compressor is provided with pump cylinder main body (20) and pump piston (25), and wherein pump cylinder main body (20) contains two ends by the 1st and the 2nd pumping cylinder lid (23 ₁, 23 ₂) cylinder-bore (24) of closing, pump piston (25) is provided with the 1st and the 2nd piston termination (25 at two ends ₁, 25 ₂), at itself and the 1st and the 2nd pumping cylinder lid (23 ₁, 23 ₂) between be divided into separately the 1st and the 2nd pump chamber (36 respectively ₁, 36 ₂) and be entrenched on the cylinder-bore (24) with being free to slide; It is characterized in that: on this pump piston (25), form and connect two piston terminations (25 ₁, 25 ₂) working room (37), the crankpin (26a) and the connecting rod (40) of pump crankcase (26) are set on this working room (37), this pump crankcase (26) is connected with rotary driving source (E); Bearing part freedom on the clutch shaft bearing hole (40a) that this connecting rod (40) forms by an end that is contained in connecting rod (40) joltily is connected on this crankpin (26a), simultaneously, the bearing part and the piston of the 2nd bearing hole (40b) that forms by the other end that is contained in connecting rod (40), freedom joltily is connected on the wrist pin (39) that pump piston (25) locates to be provided with, rotation forcing pump piston (25) to-and-fro motion by pump crankcase pin (26), and, go up the accumulator (46) that forms the lubricant oil of packing at connecting rod (40), simultaneously, make this accumulator (46) and the 1st and the 2nd bearing hole (40a, 40b) be communicated with.

2. as the double moving piston type compressor of claim 1 record, it is characterized in that:

At each pumping cylinder lid (23 ₁, 23 ₂) on, be provided with each pump chamber (36 ₁, 36 ₂) open valve when reducing pressure, gas is sucked each pump chamber (36 ₁, 36 ₂) suction valve (61a), and each pump chamber (36 ₁, 36 ₂) open valve when boosting from each pump chamber (36 ₁, 36 ₂) discharge the expulsion valve (63a) of gas.

3. as the double moving piston type compressor of claim 1 record, it is characterized in that:

On first and second bearing hole (40a, 40b), each bearing part of clamping is installed, seals the 1st and the 2nd sealed member (43,44) of this bearing hole.

4. as each described double moving piston type compressor of claim 1-3, it is characterized in that: described bearing part is a needle bearing.

5. as each described double moving piston type compressor of claim 1-3, it is characterized in that: described pump piston has smooth continuous cylndrical surface.

6. double moving piston type compressor as claimed in claim 4 is characterized in that: described pump piston has smooth continuous cylndrical surface.

7. as the double moving piston type compressor of claim 1 record, it is characterized in that:

Pump crankcase (26) free rotary ground supporting on pump cylinder main body (20).

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