CN101813086A

CN101813086A - Positive displacement pump and possess the volume fluid machine of this positive displacement pump

Info

Publication number: CN101813086A
Application number: CN201010115744A
Authority: CN
Inventors: 坪野勇; 藤村和幸; 岛田敦; 村上晃启
Original assignee: Hitachi Appliances Inc
Current assignee: Hitachi Global Life Solutions Inc
Priority date: 2009-02-12
Filing date: 2010-02-12
Publication date: 2010-08-25
Anticipated expiration: 2030-02-12
Also published as: KR101194475B1; CN101813086B; JP4920708B2; JP2010185358A; KR20100092389A

Abstract

The invention provides when the pump action is continued smoothly, be suitable for small capacity and reduce the positive displacement pump of manufacture cost and possess the volume fluid machine of this positive displacement pump.Positive displacement pump (30) possesses: the rotary work cylinder (30b) that has pump groove (30b1) and can rotatablely move; Movable fit forms the piston that circles round (30a) of two pump chambers in the pump groove.It can be that the center is rotated motion with the clutch release slave cylinder running shaft (γ) of offset Es that the rotary work cylinder is configured to, pump groove and clutch release slave cylinder running shaft (γ) are crossed as straight line shape and extend, the cylinder configuration of circling round is carried out spinning motion for carrying out circumnutation ground with radius of gyration Ep, and radius of gyration Ep and offset Es are about equally.The number that is embedded in the piston that circles round of rotary work cylinder is one, positive displacement pump has the qualification of rotation mechanism, this rotation limits mechanism and keeps the rotation of circling round of the piston that circles round and rotary work cylinder, and the speed of circling round of the piston that will circle round is defined as two times of rotational speed of rotary work cylinder.

Description

Positive displacement pump and possess the volume fluid machine of this positive displacement pump

Technical field

The present invention relates to make the positive displacement pump of the rotary work cylinder formula that the rotary work cylinder rotates with the piston that circles round that circles round and possess the volume fluid machine of this positive displacement pump, relate in particular to and successfully to continue the positive displacement pump of pump action and to possess the volume fluid machine of this positive displacement pump with small capacity and low manufacture cost.

Background technique

As the positive displacement pump of rotary work cylinder formula, shown in the disclosed hermetic type compressor of Japanese kokai publication hei 11-125191 communique (patent documentation 1), be the different plural structure of piston of phase place of circling round in the setting of a rotary work cylinder.

[patent documentation 1] Japanese kokai publication hei 11-125191 communique

In the positive displacement pump of this rotary work cylinder formula, the gap of each several part is 0, and then, when the radius of gyration Ep of the piston axis of rotation that circles round is consistent with the offset Es of clutch release slave cylinder running shaft, set up the relation of following formula (1) between the amount of the circling round Δ Ф p of the piston that circles round in the time arbitrarily and the rotating amount Ф s of rotary work cylinder all the time.In addition, for the rotating amount of rotary work cylinder, below mainly the rotation amount of meront is called rotating amount.But, according to circumstances, rotating amount is changed speech is called the rotation amount.In addition, for speed and central shaft similarly, rotational speed is suitably changed speech be called speed of autorotation, running shaft is suitably changed speech be called the axis of rotation.

Фs＝Фp/2………………………………(1)

With the both sides of this formula (1) divided by time t, thus can be with formula (1) with following formula (2) performance.

Фs/t＝(Фp/t)/2……………………(2)

In addition, represent with Ω p, the rotational speed of rotary work cylinder is represented with Ω s, then formula (1) can be showed with following formula (3) as if the speed of circling round of the piston that will circle round.

Ωs＝Ωp/2………………………………(3)

When the relation of this formula (1) or formula (3) because of some reason when untenable, be difficult to return to normal relation, consequently, the pump action can not continue, the positive displacement pump locking.

Yet usually, the circumnutation of the piston that circles round is by realizing with the rotation of radius of gyration as the bent axle of offset.Thus, the positive displacement pump of rotary work cylinder formula has following feature.

The first, the cam pin portion of bent axle and rotary work cylinder must satisfy the relation of described formula (1) or formula (3), therefore, must become the structure that can rotate (relative rotational is Ω p/2) relatively.Particularly, following structure need be set, that is, the profile of the piston that circles round be made as drum and can make between the pump groove of circle round piston outer circumferential face and rotary work cylinder and rotate; Maybe can making circles round rotates between piston inner peripheral surface and the crankshaft eccentric pin portion.

Second, in the positive displacement pump of rotary work cylinder formula, the radius of gyration Ep of piston and the offset Es of rotary work cylinder owing to circle round (apart from the offset of the centre of gyration of the piston that circles round) are identical, therefore, in once the circling round of the piston that circles round, the piston axis of rotation that circles round is only once consistent with the running shaft of rotary work cylinder.

In the positive displacement pump of rotary work cylinder formula, owing to have these features, so, by described formula (1) or the invalid situation of formula (3) on the mechanism described later generation principle.Thinking is false this formula (1) or formula (3) to produce frequency lower for situation, thereby considers to come with simple countermeasure corresponding.But, in physical device, test as can be known, owing to be located at the error of gap between key element or key element configuration (assembling), described formula (1) or the invalid situation of formula (3) frequently take place, and must take to be used to avoid the countermeasure completely of the locking that pump moves.

Below, described formula (1) or the invalid principle of formula (3) mechanism at first are described, afterwards, the mechanism of physical device is described.

At first, use Figure 17 explanation of expression principle pump action to make invalid mechanism on described formula (1) or formula (3) principle.This Figure 17 shows the position of the circle round piston and the rotary work cylinder of per 45 degree when the dextrorotation of cam pin portion is turned around.At this, the angle in the outside of being put down in writing among the figure (boldface letter) is the amount of circling round of cam pin portion, for considering cam pin portion and circling round the gapless ideal situation of piston space, therefore equates with Ф p.In addition, inboard angle (light face) is from the amount of circling round of the piston axis of rotation that circles round (cam pin portion central shaft) of the running shaft observation of rotary work cylinder, for considering to circle round gapless ideal situation between piston and pump groove, therefore equates with Ф s.In above-mentioned each moment, except unique exception described later, according to geometric relation, the rotating amount Ф s of rotary work cylinder is restricted to angle shown in Figure 17 with respect to the amount of the circling round Ф p of the piston that circles round, and therefore, described formula (1) or formula (3) are set up.

Above-mentioned exception is meant as second feature of the positive displacement pump of rotary work cylinder formula, is described clutch release slave cylinder running shaft (axis of rotation) and circle round the consistent moment of the piston axis of rotation (Figure 17 (I5)).Because the axis of rotation unanimity of two pump parts, according to described first feature, under the situation of do not circle round at the piston that circles round (Ω p=0), the rotary work cylinder can rotate (Ω s ≠ 0).Thus, by following (I) situation, may produce the unfavorable condition of (II).

(I) stop at the running shaft of the rotary work cylinder moment pump consistent with the axis of rotation of the piston that circles round.

(II) the rotary work cylinder is applied any rotation torque, under the situation of described (I), the piston that the circles round rotary work cylinder rotation of only not circling round.

If change state by this mechanism, then be absorbed in described formula (1) or the invalid situation of formula (3) as Figure 18.In addition, in case be absorbed in this situation, piston will circle round even circle round, and shown in the arrow of Figure 19, the power that imposes on the rotary work cylinder produces towards the direction of the running shaft by (the rotary work cylinder that produces at described (II) rotate to be any angle of swing) rotary work cylinder.Therefore, do not have to produce the torque that the rotary work cylinder is changeed, can not recover the rotary work cylinder naturally and carry out from transferring the regular posture that described formula (1) or formula (3) are set up.Consequently, positive displacement pump locking.For fear of this pump locking, need effectively and simply to avoid described (I) as can be known.For example, can use slot effect, determine the set angle of motor in pump non-stop mode under the state of described (I) as the motor of driving source.

Below, cause described formula (1) or the invalid mechanism of formula (3) under the situation of physical device are described.According to described principle mechanism as can be known, locking is the prerequisite that is produced as with described (I), but in fact, even the situation of described (I) do not occur, locking also frequently takes place.That is, exist the locking of not derived in the principle investigation to produce mechanism.Therefore, the locking generation mechanism that changes physical device investigates.That is, in the pump action, investigate the rotary work cylinder and produce the mechanism of the rotation outside described formula (1) or the formula (3).

Use Figure 19, Figure 20 to describing as the principal organ of reason with the cam pin portion and the gap of circling round between the piston.Figure 19 is the figure that the influence that cam pin portion and the gap between the piston of circling round are brought to pump action is described.In Figure 19, this gap enlargement is illustrated.Figure 19 (R3)～(R5) expression and the identical moment of Figure 17 (I3)～(I5).

Circle round piston owing to separate the suction side pump chamber and ejection side pump chamber, therefore, bear from the power of working fluid towards the direction of arrow of Figure 19.Therefore, circle round piston according to cam pin portion and the gap between the piston of circling round, to the direction displacement of this power.Exaggerate showing described displacement among Figure 19, the piston axis of rotation that circles round under this situation is represented with filled circles.In addition, the cam pin portion central shaft under each situation is is also surveyed and drawn with quadrilateral.After Figure 19 (R5), cam pin portion left side downwards moves, and therefore, the filled circles after this necessarily is moved to the left.Consequently, the axis of rotation track of the piston that circles round does not pass through the running shaft of rotary work cylinder, and by its left side.Figure 20 shows the track that amplifies this piston axis of rotation that circles round.

And then the power that acts on the piston that circles round makes the rotation of rotary work cylinder with the power from described working fluid, therefore, be applied to the rotary work cylinder power reaction force to the rectangular directive effect of pump groove.Thus, the displacement that among Figure 20 this reaction force is caused is is further surveyed and drawn with open circles the axis of rotation position of the altered piston that circles round.Under the effect from the reaction force of this rotary work cylinder, the axis of rotation track of the piston that circles round is offset more to the left as can be known.Because the direction that connects the rectilinear direction of circle round the piston axis of rotation and clutch release slave cylinder running shaft and be the pump groove (promptly, the rotatable phase of rotary work cylinder), therefore, near rotary work cylinder (clutch release slave cylinder running shaft with the axis of rotation consistent location of piston of circling round) in its vicinity as can be known, the possibility that has the rotation (particularly, sense of rotation is from the urgent counterclockwise counter-rotating of clockwise direction) that produces outside described formula (1) or the formula (3).Promptly as can be known, there is the possibility that causes the rotation outside described formula (1) or the formula (3) and lock in cam pin portion and circle round gap between the piston in pump action.

On the contrary, also can carry out following explanation, near consistent location on the axis of rotation principle of the running shaft of rotary work cylinder and the piston that circles round,, the possibility that becomes regular pump action under situation about not locking be arranged also even both are inconsistent according to this investigation.Promptly, the gap of the pump groove of piston and rotary work cylinder is little if the deviation ratio of the axis of rotation track of the running shaft of rotary work cylinder and the piston that circles round is circled round, then can be under the situation of the direction that does not change the pump groove, the axis of rotation that makes the piston that circles round by from the central shaft of pump groove away from the position, the pump action is continued.

Be the axis of rotation of instigating the piston that circles round at the axis of rotation of the clutch release slave cylinder running shaft of this narration and the piston that circles round by from the central shaft of pump groove away from the instantaneous axis of moment of position.

As described above, under the situation that as between the pump constituting component, has the physical device the gap, the gap, abridged produces as reason in described formula (1) or the invalid situation of formula (3) when principle is investigated, and also produces the effect of revising described formula (1) or the invalid situation of formula (3) by the gap.Same situation also produces because of the configuration error of gap between other key element of described not explanation or key element (the radius of gyration Ep of the piston axis of rotation that circles round and the offset Es of clutch release slave cylinder running shaft are inconsistent etc.).So, described formula (1) or formula (3) are false, and the action of pump is locked under the condition of gap between any key element or key element configuration and produces, or determines under the combination of various situations, therefore, is difficult to take some countermeasures according to each locking generation situation.

Thus, the action locking for fear of the positive displacement pump of rotary work cylinder formula continues action smoothly, is necessary to set the pass that makes described formula (1) or formula (3) and ties up to the rotation that rotary work cylinder and the piston space that circles round set up all the time and limit mechanism.And, also need the relation of strict constraint described formula (1) or formula (3), and satisfy the rotation qualification mechanism of the condition of following (A), (B).

(A) the rotary work cylinder and the piston that circles round are made as mechanism beyond the existing rotating mechanism of the relation that limits described formula (1) or formula (3).

(B) at the running shaft of rotary work cylinder near moment consistent with the axis of rotation of the piston that circles round, the restriction of relation that both configuration is defined as described formula (1) or formula (3) is also the strongest, this constantly outside, its restriction is relaxed.

For fear of action locking, described patent documentation 1 phase place of having taked to circle round is the countermeasure that two different pistons that circle round of 180 degree are located at a rotary work cylinder.This is thoroughly to solve of countermeasure, along with the axis of rotation of the piston that circles round of a side running shaft near the rotary work cylinder, the axis of rotation of the piston that circles round of opposite side apart from the running shaft of rotary work cylinder farthest, the rotation that described condition (A), (B) are satisfied in the combination of circle round piston and pump groove performance mutually limits the effect of mechanism.

But, two pistons that circle round of this Technology Need, therefore unbecoming with small capacityization.And then, owing to increased the parts number of packages, cause processing cost to increase.And, and then the assembling performance of the following stated significantly reduces.Bent axle has the cam pin portion at two eccentric on the different direction of 180 degree positions, and it almost is impossible inserting it into the rotary work cylinder that is set with two pump grooves on the different direction of 90 degree.For example, if be designed to extremely little with respect to the pump well width offset and the diameter of cam pin portion, then be possible geometrically, but in order to ensure pressing quantity (giving as security the け amount of removing), must increase the external diameter and the height of the piston that circles round, the load that produces cam pin portion increases, and makes reliability and performance significantly reduce.Therefore, except that cutting apart the rotary work cylinder, they are inserted respectively after the cam pin portion of bent axle, need carry out the assembling procedure of incorporate complexity with high positional accuracy, the problem that exists manufacture cost to rise.

Summary of the invention

The object of the present invention is to provide a kind ofly when pump action is continued smoothly, be suitable for small capacity and can reduce the positive displacement pump of manufacture cost and use the volume fluid machine of this positive displacement pump.

In order to realize aforementioned purpose, first scheme of the present invention provides a kind of positive displacement pump, and it possesses: pump case, and it has shell chamber; The rotary work cylinder, it has the pump groove, and is configured to and can rotatablely moves in described shell chamber; Piston circles round, its gap is embedded in described pump groove and separates this pump groove, thereby form two pump chambers, described circle round piston or described rotary work cylinder utilize driving source to carry out circumnutation or rotatablely move, the rotary work cylinder can be that the center is rotated motion with the clutch release slave cylinder running shaft, this clutch release slave cylinder running shaft is Es with respect to the offset of piston rotary shaft as the central shaft of the circumnutation of the piston that circles round, described pump groove intersects with clutch release slave cylinder running shaft as the central shaft that rotatablely moves of described rotary work cylinder and extends with straight line shape, the described piston to-and-fro motion in described pump groove of circling round, and can carry out circumnutation ground with radius of gyration Ep with respect to described pump case and carry out spinning motion, the radius of gyration Ep of the described piston that circles round and the offset Es of described rotary work cylinder are about equally, wherein, the quantity that is embedded in the described piston that circles round of described rotary work cylinder is made as one, described positive displacement pump also has the qualification of rotation mechanism, this rotation limits the rotation that mechanism keeps circling round of the described piston that circles round and described rotary work cylinder, and the speed of circling round of this piston that circles round is defined as 2 times of rotational speed of this rotary work cylinder.

The preferred concrete structure of first scheme of the invention described above is as described below.

(1) makes expenditure less than making expenditure in circled round the qualification that described rotation during angle of circling round of 180 degree limits mechanism of described piston rotary shaft in the qualification of the described piston rotary shaft described rotation qualification mechanism during angle of circling round consistent with described clutch release slave cylinder running shaft.

(2) be the circumnutation that the bent axle of Ec is realized the described piston that circles round by offset,

By offset is the running shaft that the bearing portion of Eb realizes described rotary work cylinder,

Below 2 times of difference of the offset Eb of offset Ec that described gap of circling round between piston and the described pump groove is described bent axle and described bearing portion.

(3) described rotation limits mechanism and possesses: make the rotation of the described piston that circles round and the synchronous rotating synchro structure of rotation of described rotary work cylinder; The speed of circling round of the described piston that circles round is defined as 2 times piston rotation qualification mechanism of speed of autorotation.

(4) described rotating synchro structure constitutes by being provided with the par, side at the described piston that circles round, and the bi-side of this par, side and described pump groove are slidingly connected respectively.

(5) described piston rotation limits mechanism and possesses slide-block mechanism, this slide-block mechanism limits the motion of the described piston that circles round, make on the circumnutation track of the described piston axis of rotation that circles round, be in all the time by on the straight line on the described piston that circles round of described being fixed in of the piston axis of rotation of circling round with the rest point of described clutch release slave cylinder running shaft diverse location.

(6) described rest point is arranged at the position that the position from described clutch release slave cylinder running shaft on the described circumnutation track has rotated 180 degree.

(7) described slide-block mechanism possesses not movable slider and rotation guide,

Described not movable slider realized by the fixed-site cylinder, and described fixed-site cylinder fixed configurations is in the position corresponding with described rest point of described pump case,

The rotation guide realizes that by at the described piston that circles round steering channel being set this steering channel is that center line and described fixed-site cylinder constitute sliding pair with described straight line, has and the equal width of the diameter of described fixed-site cylinder.

(8) described not movable slider possesses: fixed center axis; Slider part, it inserts this fixed center axis and rotates freely.

(9) with the path of described steering channel as working fluid.

(10) described steering channel is extended to par, described side.

(11) be equipped on described volume fluid machine as oily supply source from oil to the each several part of volume fluid machine that supply with.

In addition, alternative plan of the present invention provides a kind of volume fluid machine, and it possesses: driving source; Bent axle by described driving source driving; By the positive displacement pump of described crank-driven, described positive displacement pump possesses: pump case, and it has shell chamber; The rotary work cylinder, it has the pump groove and is configured to and can rotatablely move in described shell chamber; Piston circles round, its gap is embedded in described pump groove and separates this pump groove, thereby form two pump chambers, described circle round piston or described rotary work cylinder utilize described driving source to carry out circumnutation or rotatablely move, the rotary work cylinder can be that the center is rotated motion with the clutch release slave cylinder running shaft, this clutch release slave cylinder running shaft is Es with respect to the offset of piston rotary shaft as the central shaft of the circumnutation of the piston that circles round, described pump groove intersects with clutch release slave cylinder running shaft as the central shaft that rotatablely moves of described rotary work cylinder and extends with straight line shape, the described piston that circles round moves back and forth in described pump groove, and can carry out circumnutation ground with radius of gyration Ep with respect to described pump case and carry out spinning motion, the radius of gyration Ep of the described piston that circles round and the offset Es of described rotary work cylinder are about equally, wherein, the quantity that is embedded in the described piston that circles round of described rotary work cylinder is made as one, described volume fluid machine is provided with to rotate and limits mechanism, this rotation limits the rotation that mechanism keeps circling round of the described piston that circles round and described rotary work cylinder, and the speed of circling round of this piston that circles round is defined as 2 times of rotational speed of this rotary work cylinder.

According to the present invention, can provide a kind of when pump action is continued smoothly, be suitable for small capacity and can reduce the positive displacement pump of manufacture cost and use the volume fluid machine of this positive displacement pump.

Description of drawings

Fig. 1 is the longitudinal sectional drawing of the scroll compressor that relates to of first mode of execution of the present invention.

Fig. 2 is near the detailed enlarged view of back pressure chamber of the scroll compressor of Fig. 1.

Fig. 3 is the enlarged elevation figure of oil feed pump of the scroll compressor of Fig. 1.

Fig. 4 is the K-K profile of Fig. 3.

Fig. 5 is the V-V sectional drawing of Fig. 4.

Fig. 6 A is near the enlarged elevation figure of the variation 1 the fixed-site cylinder of oil feed pump of scroll compressor of Fig. 1.

Fig. 6 B is near the enlarged elevation figure of the variation 2 the fixed-site cylinder of oil feed pump of scroll compressor of Fig. 1.

Fig. 7 is the plan view of substrate of oil feed pump of the scroll compressor of Fig. 1.

Fig. 8 be changed Fig. 1 scroll compressor oil feed pump the fixed-site cylinder position and the transverse cross-sectional view when circling round the piston side view be set.

Fig. 9 is the parts open cube display of oil feed pump of the scroll compressor of Fig. 1.

Figure 10 is the action specification figure of oil feed pump of the scroll compressor of Fig. 1.

Figure 11 is the rotating synchro structure of oil feed pump of scroll compressor of Fig. 1 and the explanatory drawing that piston rotation limits mechanism.

Figure 12 is the enlarged elevation figure of fixed-site cylinder of the oil feed pump of the scroll compressor that relates to of second mode of execution of the present invention.

Figure 13 is the L-L profile of Figure 12.

Figure 14 is the amplification transverse cross-sectional view of fixed-site cylinder of the oil feed pump of the scroll compressor that relates to of the 3rd mode of execution of the present invention.

Figure 15 is near the detailed enlarged view the back pressure chamber of the scroll compressor that relates to of the 4th mode of execution of the present invention.

Figure 16 is the vertical sectional view of amplification of the oil feed pump of the scroll compressor that relates to of the 4th mode of execution of the present invention.

Figure 17 is the explanatory drawing that the principle pump of the positive displacement pump of rotary work cylinder formula moves.

Figure 18 is the explanatory drawing that carries out the pump action outside the principle with the positive displacement pump of rotary work cylinder formula.

Figure 19 is an example of the pump action outside the actual principle is carried out in expression with the positive displacement pump of rotary work cylinder formula a explanatory drawing.

The figure of the circle round piston centrode of Figure 20 when to be expression with the positive displacement pump of rotary work cylinder formula carry out pump action outside the actual principle.

Figure 21 is the explanatory drawing that expenditure is made in the qualification of rotary work cylinder angle of rotation of oil feed pump of the scroll compressor of Fig. 1.

The figure of the track of the piston that circles round when Figure 22 is the pump groove of oil feed pump of scroll compressor of presentation graphs 1 and difference that the gap between the piston of circling round is Eb and Ec 2 times.

Symbol description:

1 ... scroll compressor

2 ... the fixed eddy plate parts

3 ... the whirlpool disk component circles round

4 ... framework

5 ... European ring (ォ Le ダ system リ Application ゲ)

6 ... bent axle

6b ... oil supply hole

6f ... pump shaft portion

6f1 ... the pump eccentric part

7 ... motor

22 ... bypass valve

26 ... the back pressure control valve

30 ... oil feed pump

30a ... piston circles round

30a5 ... flat end

30a6 ... the piston bearing hole

30b ... the rotary work cylinder

30b1 ... the pump groove

30b4 ... end plate

30c ... pump case

30c4 ... shell chamber

30d ... pump ejection stream

30g ... steering channel

30h ... the par, side

30p ... the fixed-site cylinder

30p4 ... roller

30p5 ... slide roller

30s ... the pump suction passage

100 ... pressing chamber

105 ... suction chamber

110 ... back pressure chamber

120 ... the ejection chamber

125 ... store oil portion

140 ... pump chamber

140s ... suck pump chamber

140d ... the ejection pump chamber

α ... piston rotary shaft (crankshaft rotating axle)

β ... pump eccentric part central shaft

β ' ... the piston axis of rotation circles round

γ ... clutch release slave cylinder running shaft (the clutch release slave cylinder axis of rotation)

Embodiment

Below, in conjunction with the accompanying drawings to positive displacement pump of the present invention is described as a plurality of mode of executions under the situation of the oil feed pump of supplying with oil as the bearing or the pressing chamber of the scroll compressor of volume fluid machine (with working fluid as oil).Prosign among the figure of each mode of execution is represented same thing or suitable thing.In addition, the present invention also comprises and as required each mode of execution is suitably made up and obtain further effectively effect.In addition, after, the working fluid in the positive displacement pump of the present invention is defined in the oil, therefore, is called oil, and the address of working fluid is meant the working fluid of scroll compressor.

(first mode of execution)

Use Fig. 1～Figure 11 explanation store oil portion to be set, first mode of execution that in housing, in the scroll compressor of formation suction pressure positive displacement pump of the present invention is carried as oil feed pump in housing.Like this, the so-called low-pressure cavity type as constitute suction pressure in housing can exemplify the situation of inflammable gas as working fluid.For example, hydrocarbon system such as propane or butane fluid is suitable with it.This is from the Security viewpoint, is used for inclosure is comprised the effective means that the total amount of working fluid of the device integral body of compressor reduces.

At first, near the enlarged view that uses (the N portion of Fig. 1) back pressure chamber of longitudinal sectional drawing, Fig. 2 of the scroll compressor that first mode of execution of the present invention of Fig. 1 relates to describes the overall structure and the action of the scroll compressor of present embodiment.In addition, use Fig. 3～Figure 11 to describe the oil feed pump of present embodiment afterwards in detail.

The side that suction pipe 53 connects housing 8 is provided with, and the working fluid of suction pressure is imported in the housing 8 by this suction pipe 53.And this working fluid is to the suction port 2e of the lateral opening of fixed eddy plate 2 guiding pressing chamber 100, and this pressing chamber 100 is formed on fixed eddy plate 2 and circles round between the whirlpool dish 3.This pressing chamber 100 utilizes the circumnutation of the whirlpool dish 3 that circles round to dwindle volume when the inside perimembranous of peripheral part moves, and therefore, the working fluid in the pressing chamber 100 is compressed.At this, the circumnutation of the whirlpool dish 3 that circles round is by utilizing motor 7 to make to circle round 6 rotations of whirlpool dish 3 bent axles that connected, and prevented from transferring realization by European ring 5.

Be provided with at the upper surface of fixed eddy plate 2 and be used to the bypass valve 22 of avoiding overcompression or hydraulic pressure to contract, and, the ejiction opening 2d that makes compressed working fluid ejection be provided with.Fixed eddy plate 2 screw threads are fixed in framework 4.Between the back side of the whirlpool dish 3 that circles round and framework 4, be formed with the back pressure chamber 110 that constitutes intermediate pressure (pressure of suction pressure and the centre that sprays pressure is hereinafter referred to as back pressure).

Bent axle 6 is equipped on framework axial projections 6p by axle alar part 6h and limits the axle direction position, and top is by main bearing 24 supportings, and its underpart is by supplementary bearing 25 supportings.The 6a of cam pin portion that is located at the upper end of bent axle 6 inserts the bearing 23 that circles round of the whirlpool dish 3 that circles round.At this, supplementary bearing 25 is made of roller 25a and roller rolling retainer 25b.Roller rolling retainer 25b is welded in the countershaft supporting member of fixing at housing 8 50.The structure that utilization is made of this roller 25a and roller rolling retainer 25b can allow the inclination of countershaft supporting member 50 on a certain degree.

The oil that will draw from the store oil portion 125 of housing 8 bottoms with oil feed pump 30 is supplied in above-mentioned bearing by the oil supply hole 6b of bent axle 6.The oil of supplying with to circle round bearing 23 and main bearing 24 enters back pressure chamber 110, then, flows out road 135 by the back pressure chamber that connects framework 4 and flows out to the side of framework 4, finally returns store oil portion 125.At this, in the way on back pressure chamber outflow road 135, be provided with back pressure control valve 26.This back pressure control valve 26 remains required back pressure with the pressure of back pressure chamber 110.Utilize this back pressure, the whirlpool dish 3 that will circle round when compression is to fixed eddy plate 2 application of forces.

On the other hand, in order to improve the sealing of pressing chamber 100, bearing chamber 115 is supplied with a spot of oil by pressing chamber fuel feeding road 130 to pressing chamber 100 from circling round.This oil sprays to fixed eddy plate 2 tops from ejiction opening 2d or bypass valve 22 with working fluid as ejection oil.

Ejection oil separates and returns oily clutch release slave cylinder 55 and be fixed in the top of fixed eddy plate 2 by screw thread, and is formed with ejection chamber 120 on the top of fixed eddy plate 2.Separate the top screw thread that returns oily clutch release slave cylinder 55 at ejection oil and be fixed with ejection cover 51, form oil separation chamber 90 and oil revolute chamber 95 with further outstanding spraying pipe 52.

With flowing into the working fluid guiding oil separation chamber 90 of ejection chamber 120, after the oil that will sneak into this working fluid separates, make working fluid pass through spraying pipe 52 and outside compressor 1, flow out.Flow into oil revolute chamber 95 at oil separation chamber 90 separated oil.And the oil of inflow oil revolute chamber 95 returns store oil portion 125 via connecting oil revolute chamber 95 with the oil circuit 80 of store oil portion 125 and the recirculating oil quantity adjustment valve 70 that is arranged in its way.It is valves of bearing following effect that recirculating oil quantity is adjusted valve 70,, is used to seal the ejection side and the suction side of the both sides of oil circuit 80 that is, and guaranteeing all the time has a spot of oil in the oil revolute chamber 95, and the oil that makes and flow into the oil mass same amount of oil revolute chamber 95 simultaneously returns store oil portion 125.This recirculating oil quantity is adjusted valve 70 and is comprised that by float valve or utilization the sensor signal of the information of separating oil mass controls the solenoid valve of aperture and wait and realize.

The oil feed pump 30 of present embodiment is except that bearing that the oil that will be positioned at store oil portion 125 each bearing portion to the bent axle 6 that is made of supplementary bearing 25, main bearing 24, the bearing 23 that circles round supplies with or to the pressing chamber 100 of the sealing that is used to improve pressing chamber such as supplies with at original effect, also bearing the effect that produces back pressure and supply with to back pressure chamber 110.Therefore, boosting is also born in oil feed pump 30 effect of not only bearing flow.

In the present embodiment, the separating oil back pressure chamber importing road 500 that possesses the part importing back pressure chamber 110 of the separating oil that will flow into oil revolute chamber 95.And, being provided with separating oil branch 501, this separating oil branch 501 adjusts oil and imports the flow that flows in road 500 to described separating oil back pressure chamber.Even the situation of the back pressure amount of boost deficiency of being undertaken by oil feed pump 30 enters back pressure chamber 110 by the separating oil that ejection is pressed back pressure is risen, has the effect that the compressor performance that can avoid being caused because of the back pressure deficiency reduces.As the simplest realization mechanism of this separating oil branch 501, known have a different branched pipe in pipe arrangement footpath.

In addition, also can separating oil branch 501 is integrated with back pressure control valve 26, be provided with when back pressure does not rise, carry out separating oil is imported the separating oil importing back pressure control valve of the action of back pressure chamber 110 and so on.Under this situation, only when the back pressure rising of being undertaken by oil feed pump is not carried out, make separating oil enter back pressure chamber 110.Thus, need not to make all the time the separating oil of high temperature to enter back pressure chamber 110, have the heating that suppresses pressing chamber 100, improve the effect of compressor performance.

Then, use the detailed structure and the action of Fig. 3 to Figure 11, Figure 21,22 pairs of oil feed pumps 30 to be elaborated.This oil feed pump 30 be with as the motor 7 of the power source of scroll compressor 1 as driving source, with the piston 30a that circles round as driving side, with the positive displacement pump of rotary work cylinder 30b as the rotary work cylinder formula of slave end.

At first, use Fig. 3 to Fig. 9 that the structure of oil feed pump 30 is described.Fig. 3 is that the longitudinal sectional drawing of oil feed pump 30 (is the M portion amplification details drawing of Fig. 1, the H-H sectional drawing of Fig. 4), Fig. 4 is the transverse cross-sectional view (the K-K sectional drawing of Fig. 3) of oil feed pump 30, Fig. 5 is the longitudinal sectional drawing different with Fig. 3 (the V-V sectional drawing of Fig. 4) of oil feed pump 30, Fig. 6 A is substrate 30c1 and the enlarged elevation figure of the fixing part of fixed-site cylinder 30p independently, Fig. 6 B is and the substrate 30c1 of Fig. 6 A different modes and the enlarged elevation figure of the fixing part of fixed-site cylinder 30p independently, Fig. 7 is the plan view of substrate 30c1, Fig. 8 is the transverse cross-sectional view of the oil feed pump 30 when having changed the position being set and circling round the side view of piston 30a of fixed-site cylinder 30p, and Fig. 9 is the parts open cube display of oil feed pump 30.

Be provided with the 6f of pump shaft portion in thin footpath in the underpart of bent axle 6, be provided with pump eccentric part 6f1 in the bottom of the 6f of this pump shaft portion.The piston bearing hole 30a6 that this pump eccentric part 6f1 movable fit forms in the central part at the piston 30a that circles round.The piston 30a that circles round carries out circumnutation by the off-centre rotation of the pump eccentric part 6f1 of bent axle 6 with radius of gyration Ep.Oil supply hole 6b is at the lower end surface opening of pump eccentric part 6f1.

Be provided with and rotate rotary work cylinder 30b freely, this rotary work cylinder 30b will with respect to the rotary shaft α of the piston 30a that circles round with the axle of radius of gyration Ep offset Es off-centre about equally as running shaft γ.This rotary work cylinder 30b has pump groove 30b1, and is configured to and can be rotated motion in the shell chamber 30c4 of pump case 30c.Pump groove 30b1 is that clutch release slave cylinder running shaft γ intersects with the central shaft that rotatablely moves of rotary work cylinder 30b, and extends with straight line shape.Circle round piston 30a movable fit in pump groove 30b1, and be configured to can to-and-fro motion, by separating this pump groove 30b1, the space of the both sides of the piston 30a that circles round is formed as two pump chambers 140.The number that is embedded in the piston 30a that circles round of rotary work cylinder 30b is one.

At this, the interval between the central shaft β of pump eccentric part 6f1 and the running shaft α of bent axle 6 roughly limits the radius of gyration Ep of the piston 30a that circles round.Yet owing to have the gap between pump eccentric part 6f1 and the piston bearing hole 30a6, therefore, usually, the piston 30a basis of circling round is applied to the radial force (power that will narrate in the problem that described invention will solve is with reference to Figure 19,20) of the piston 30a that circles round and displacement.Therefore, the interval Ec of the central shaft β of pump eccentric part 6f1 and crankshaft rotating axle α (omit Ec mark) is from as the central shaft (axis of rotation that this can regard the piston that circles round as is labeled as β ') of piston bearing hole 30a6 and the radius of gyration Ep skew of the distance of crankshaft rotating axle α.

According to Fig. 9 as can be known, this piston 30a that circles round has flat end 30a5 in one end (lower end surface), and, have parallel two sides par 30h in the side and connect two side barrel surface 30a4 of above-mentioned two sides par 30h.As can be known clear and definite by Fig. 8, stagger in the mutual axle center of barrel surface 30a4, two sides, consistent with the barrel surface that forms clutch release slave cylinder chamber 30c4.Thus, the volume of the pump chamber 140 of formation is contracted to 0 on principle, therefore, do not have dead space volume, has the effect that improves performance.

Have steering channel 30g at flat end 30a5, this steering channel 30g makes that side space is communicated with piston bearing hole 30a6 under the lower surface, and, stride two sides par 30h and extend.The width of this steering channel 30g is fixed.As mentioned above, be provided with and rotate rotary work cylinder 30b freely, this rotary work cylinder 30b will from piston rotary shaft α with the axle of the roughly the same offset Es off-centre of the radius of gyration Ep of the piston 30a that circles round as running shaft γ.Thus, as shown in Figure 8, clutch release slave cylinder running shaft γ enters on the track that circles round of the piston axis of rotation β ' that circles round.Consequently, during the piston 30a that circles round turns around, only produce and once circle round the piston axis of rotation β ' and the consistent moment of clutch release slave cylinder running shaft γ.

Rotary work cylinder 30b portion in the axial direction has the 30b4 of end plate portion, and, have pump groove 30b1 in axial bottom.The piston 30a that circles round is installed on pump groove 30b1, and par, the side 30h of the piston 30a that circles round is connected and to-and-fro motion with the side slip of pump groove 30b1.Thus, pump groove 30b1 is separated into two spaces, and each space becomes pump chamber 140.This pump chamber 140 separates by the inner space of pump case 30c and housing 8.

This pump case 30c comprises: be arranged at the lower surface of rotary work cylinder 30b and the substrate 30c1 and the cover 30c2 of upper surface side respectively; Pump work cylinder 30c3 as above-mentioned linking department and swivel bearing rotary work cylinder.As shown in Figure 7, substrate 30c1 has suction mortise 30s1 that is located at upper surface and the pump inlet hole 30s2 that connects substrate 30c1, utilizes these to constitute the pump suction passage 30s that oil is picked up from store oil portion 125.And then substrate 30c1 has pump ejection mortise 30d1 and the pump ejection Ditch 30d2 that is located at upper surface, utilizes these to constitute the pump ejection stream 30d that sends oil to oil supply hole 6b, and described oil supply hole 6b is at the lower ending opening of bent axle 6.

At the central part of substrate 30c1, Tu Chu fixed-site cylinder 30p and substrate 30c1 are wholely set upward.This fixed-site cylinder 30p is located at the position that has rotated 180 ° from clutch release slave cylinder running shaft γ on the track that circles round of the axis of rotation β ' of the piston 30a that circles round.In addition, shown in Fig. 6 A and Fig. 6 B, fixed-site cylinder 30p-1,30p-2 can differently with substrate 30c1 be set separately.Fixed-site cylinder 30p-1 is made of the cylinder of same diameter, is pressed into the hole of substrate 30c1 from the top and fixes.Fixed-site cylinder 30p-1 is made of the cylinder that has flange in the lower end, is pressed into the hole of substrate 30c1 from the below and fixes.

According to Fig. 3, Fig. 5 as can be known, in the pump case 30c of present embodiment, be provided with cover 30c2 and the incorporate top of pump work cylinder 30c3 pump case 30c23.Thus, have the reduction component number, realize the effect of the raising of assembling performance.And, be provided with necessary minimal hole by pump eccentric part 6f1 at top pump case 30c23.

As shown in Figure 9, in the actual assembled of oil feed pump 30, at first, make the hole of pump eccentric part 6f1 by top pump case parts 30c23, then, the rotary work cylinder 30b that packs into, the piston 30a that circles round are temporarily fixed on roller rolling retainer 25b (also can be supplementary bearing supporting plate 50) with top pump case 30c23.

Under this state, fixed-site cylinder 30p inserts steering channel 30g, simultaneously substrate 30c1 is fixed in top pump case 30c23 by substrate set screw 30m.At this moment, insert locating stud, make the positioning hole 30i2 of substrate 30c1 consistent, improve the desired location precision of pump suction passage 30s and pump ejection stream 30d with the positioning hole 30i2 of top pump case 30c23.

After this, Yi Bian make bent axle 6 rotations, Yi Bian pump work cylinder set screw 30k is formally fastening, 30c3 is fixed in roller rolling retainer 25b with the pump work cylinder.Thus, can improve the positional accuracy of pump work cylinder 30c3, therefore, improve the positional accuracy of clutch release slave cylinder running shaft γ, can make the action of oil feed pump 30 smooth, have the effect that improves the fuel feeding pump performance.At this, as the method that makes bent axle 6 rotations, can be by making motor 7 low speed rotation or making the whirlpool disk component 3 that circles round carry out circumnutation etc. from suction port 2e suck with vacuum pump.

Below, use Figure 10, Figure 11, Figure 21 and Figure 22 that the action of oil feed pump 30 is described.Figure 10 is the action specification figure of oil feed pump 30, uses the section identical with Fig. 4 to show pump chamber 140 and carries out a pump action during the stroke.Figure 11 is the action specification figure under the situation when making the piston 30a that circles round consistent with the rotation center of rotary work cylinder 30b, Figure 21 is the explanatory drawing that expenditure is made in the qualification of rotary work cylinder angle of rotation, and Figure 22 is the track of pump groove 30b1 and the gap between the piston 30a of the circling round piston 30a that circles round when being 2 times of difference of Eb and Ec.

As shown in figure 10, during a stroke of pump chamber 140, bent axle 6 take two turns (towards the direction of arrow rotation of circle shape).In addition, in Figure 10, the profile change of bent axle 6 every rotation 22.5 degree is shown, omits the hatching of the section of each constituting component of expression.

As mentioned above, form two pump chambers 140 simultaneously.Described two pump chamber 140 phase places stagger mutually, and therefore, when the pump chamber of a side was suction stroke, the pump chamber of opposite side was the ejection stroke, but its action changes identical.Therefore, action describes to pump at a pump chamber (work of Figure 10 the pump chamber of crossing section line).In addition, pump chamber 140 is called suction pump chamber 140s when being in suction stroke, is called ejection pump chamber 140d when being in the ejection stroke.

Figure 10 (uses band bracket numeral with zero numeral of being with among the figure in specification.) (1) to (10) be suction stroke, for the oil of store oil portion 125 by suction passage 30s to sucking the operation that pump chamber 140s picks up.And (11) of Figure 10 to (16) are the ejection stroke, the operation that sprays to oil supply hole 6b by ejection stream 30d and steering channel 30g for the oil that will spray among the pump chamber 140d.Principle in the existing structure (structure that does not have newly-installed fixed-site cylinder 30p, steering channel 30g and par, side 30h in the present embodiment) (gap of each several part minimum and when not having assembly error) pump action and problem points are described as the problem (with reference to Figure 17,18) that invention will solve, and, have the pump action and the problem points of the physical device of the gap of each several part or the error in when assembling also to describe with Figure 19,20.

Therefore, after, be that Figure 10 or Figure 21 are used in the center with Figure 11, the newly-installed fixed-site cylinder of present embodiment 30p, steering channel 30g and par, side 30h are described.That is, position fixed cylinder 30p, steering channel 30g and par, side 30h are become satisfy the situation that described condition (A) and rotation (B) limit mechanism and describe.At first, can constitute the situation that satisfies described condition (A) mechanism (B) to newly-installed key element in the present embodiment describes, secondly, to the place that is provided with by these key elements of optimization, thereby the situation that satisfies described condition (B) more well describes.

For satisfy condition (A) " speed of circling round of the piston 30a that will circle round is defined as 2 times of rotational speed of rotary work cylinder 30b all the time ", at first, by having the synchronous rotating synchro structure of speed of autorotation of the rotational speed that makes rotary work cylinder 30b and the piston 30a that circles round, thereby condition (A) is converted to the condition that only limits the piston 30a that circles round.Particularly, change to 2 times the piston rotation that the speed of circling round that is provided with the piston 30a that circles round is defined as speed of autorotation and limit the such content of mechanism.

The rotating synchro structure of present embodiment is provided with two sides par 30h by the side at the piston 30a that circles round, and the pump groove 30b1 of this par, side 30h and rotary work cylinder 30b inserts with being slidingly connected and realizes.This rotating synchro structure constitutes separates the sealed department that sucks pump chamber 140s and ejection pump chamber 140d, becomes face seal by existing linear sealing, thereby also has the effect of improving sealing.

Limit mechanism as another piston rotation that constitutes mechanism and realize by slide-block mechanism, this slide-block mechanism will be disposed at steering channel (steering channel be provided with the position change of angle at the fixing pin) 30g that fixed-site cylinder 30p on the track that circles round of axis of rotation β ' of the piston 30a that circles round is inserted through the piston axis of rotation β ' that circles round.This slide-block mechanism becomes piston rotation and limits mechanism, even set this slide-block mechanism and described synchronous rotating mechanism is made up and the rotation qualification mechanism of formation, also as shown in figure 10, can carry out the action of oil feed pump as can be known.

As mentioned above, with par, the side 30h that realizes the rotating synchro structure with by realizing that piston rotation limits the mechanism that the fixed-site cylinder 30p of mechanism and slide-block mechanism that steering channel 30g constitutes made up and satisfies described condition (A).

Then, the situation of satisfy condition (B) is narrated, at first, defined as expenditure rotating the qualification that limits mechanism.Qualification is meant as expenditure can be with respect to the regulation of target and the index of the precision of regulation any degree well, is defined as the inverse of the difference of desired value and actual set value.Formula (1) shown in, orientate limit make expenditure as described by the inverse of the target rotating amount of rotary work cylinder that will be corresponding with the amount of the circling round Ф p of the piston that circles round and the error (rotating deviation) of actual rotating amount for the desired value of present embodiment.That is, become following formula (4).

Expenditure ≡ 1/ rotating deviation is made in qualification ... (4)

The main cause of rotary work cylinder rotating amount error (rotating deviation) is thought of as the gap (deviation) of fixed-site cylinder 30p and steering channel 30g.At this, this rotating deviation is made as Δ, obtain and limit the formula of making expenditure.As shown in figure 21, make the parameter of expenditure, the amount of circling round (Ф p, definition) identical with Figure 17 of set angle (angle on the track of the piston axis of rotation β ' that will circle round is made as θ) with the piston 30a that circles round of fixed-site cylinder 30p is arranged as qualification.In Figure 21, enlarge the rotating deviation Δ for convenience of explanation, the diameter of contracted position fixed cylinder 30p.As can be seen from Figure 21, the rotating deviation Δ is obtained from following formula (5) according to the deviation delta s of the circumferencial direction of radius L.

Rotating deviation Δ=Arctan (abs (Δ s/L)) ... (5)

At this, abs represents absolute value.

L in this formula (5), Δ s are made of following formula (6), (7).

L＝2·Es·cos(θ/2)……………………(6)

Δs＝Δ/cos(χ)……………………………(7)

At this, as shown in figure 21, χ connects the angle that clutch release slave cylinder running shaft γ and the line of fixed-site cylinder 30p are become with steering channel 30g.

Steering channel 30g rotational speed and rotary work cylinder 30b by clutch release slave cylinder running shaft γ, steering channel 30g when the piston axis of rotation β ' that circles round comes the position of clutch release slave cylinder running shaft γ is synchronous, and then, the rotational speed of rotary work cylinder 30b is half of the speed of circling round of piston 30a of circling round, thus, χ can be by following formula (8) as can be known.

χ＝abs(π-Фp)/2…………………………(8)

Bring formula (8) into formula (7), and bring formula (5) into, obtain the rotating deviation Δ with formula (6), last, bring formula (4) into, obtain to limit and make expenditure, become following formula (9).

Expenditure=1/ (Arctan (Δ/(2Epabs (cos (θ/2) sin (Ф p/2))))) is done in qualification ... (9)

If Ф p=π rad when utilizing formula (9) to calculate to circle round piston axis of rotation β ' consistent with clutch release slave cylinder running shaft γ, expenditure is made in the qualification that reaches Ф p=0rad when it has rotated π rad (180 spend), then becomes following formula (10), (11).

Expenditure (Ф p=π)=1/ (Arctan (Δ/(2Epabs (cos (θ/2))))) is made in qualification ... (10)

Expenditure (Ф p=0)=1/ (Arctan (∞))=2/ π is made in qualification ... (11)

Except that θ=π red, the inequality of following formula (12) is set up.

Qualification is done expenditure (Ф p=π)＞qualification and is made expenditure (Ф p=0) ... (12)

Thus, as can be known except fixed-site cylinder 30p when consistent (θ=π rad) with clutch release slave cylinder running shaft γ, the rotation of new settings limits the qualification of mechanism and makes expenditure height when making expenditure low (the piston axis of rotation β ' that circles round is consistent with clutch release slave cylinder running shaft γ) based on the qualification of drive system, and is low when making expenditure height (circled round 180 spend from circle round piston axis of rotation β ' and clutch release slave cylinder running shaft γ consistent location) based on the qualification of drive system.Thus, (B) as can be known satisfies condition.

As known from the above, even fixed-site cylinder 30p is set at any position different with clutch release slave cylinder running shaft γ, limit rotation mechanism and drive system concerted action between newly-installed piston cylinder, do to replenish when expenditure is hanged down with the qualification of a side, on the contrary, make the mode that expenditure only retrains when high in qualification, performance reduces to limit makes expenditure, realizes the effect of pump action smoothly.

In addition, as can be known clear and definite by formula (9), along with set angle θ is changed to 0rad from π rad, limits the absolute value of making expenditure and become big (when the amount of circling round Ф p is identical), 0rad becomes maximum.That is,, limit then that to make expenditure the highest, can play and suppress the rotating deviation Δ, make pump action effect more smoothly if fixed-site cylinder 30p is located at the positions that rotated 180 degree from the position of clutch release slave cylinder running shaft γ at the track of the piston axis of rotation β ' that circles round.

As can be known clear and definite from Fig. 7, Fig. 9, fixed-site cylinder 30p erects and is arranged among the pump ejection stream 30d.And steering channel 30g constitutes the ejection path that connects pump ejection stream 30d and oil supply hole 6b.Thus, the slide part of fixed-site cylinder 30p and steering channel 30g is positioned at the center of oily path all the time, therefore, plays the raising lubricity, improves the effect of reliability.

In the present embodiment, steering channel 30g is extended to par, side 30h.As mentioned above, steering channel 30g constitutes the stream of oil, and therefore, oil is present in steering channel 30g comfortably.Thus, the steering channel 30g that extends to par, side 30h constitutes fuel feeding stream from oil to par, side 30h that supply with, play the reliability that improves based on the lubricity between par, side 30h and the pump groove 30g and improve effect, and aspect the raising sealing, play reduction and improve effect to the performance of the leakage that sucks pump chamber 140s from ejection pump chamber 140d.And by steering channel 30g being extended to par, side 30h, it is identical that groove adds the action of cutter in man-hour, has the effect of the accuracy to shape that improves groove.

In addition, can be at the break-in tunicle of the surface of the piston 30a that circles round, rotary work cylinder 30b or pump case 30c setting as manganese phosphate and so on.At this moment, because running-in effect, each gap diminishes along with running, has the effect that improves sealing and improve pump performance.

In addition, in the present embodiment, the piston 30a that will circle round is made as driving side, and 30b is made as slave end with the rotary work cylinder, but opposite, also rotary work cylinder 30b can be made as driving side, and the piston 30a that will circle round is made as slave end.At this moment, the crankshaft support that piston 30a can carry out circumnutation that circles round.

In addition, in the present embodiment, pump groove 30b1 extends to the periphery of rotary work cylinder 30b.Thus, because it is identical to make groove add the action of cutter in man-hour, therefore, has the effect of the accuracy to shape that improves groove.In addition,, therefore can improve the sealing of circumferential play, therefore have the effect that pump performance improves owing to the fuel feeding that carries out to rotary work cylinder circumferential play.And then, because this pump groove 30b1 that penetrates, so end plate 30b4 necessitates, thus, become the mode of pushing the structure that can realize the 4th mode of execution described later that can suppress sideshake of utilizing, but the present invention is not limited to this, can not penetrate into periphery, but the mode of the pump grooved of the long hole shape of existing (patent documentation 1).

In addition, in the present embodiment, be located at the axle center of two barrel surface 30a4 of the side of the piston 30a that circles round and stagger, but shown in the same barrel surface shown in the single-point line of Fig. 8, also can be the barrel surface of axle center unanimity.Its reason is, the working fluid of present embodiment is the incompressible fluid that is called oil, therefore, minimizing reduces because of the performance that dead space volume caused, in addition, can after having formed barrel surface, process side view, therefore, have the effect that cuts down finished cost by cutting par, side 30h.In addition, not boosting when only carrying out this purposes of conveying of oil, become the degree that can ignore because of the caused performance of dead space volume further reduces, therefore, the piston 30a that circles round of the same barrel surface shown in the line of the single-point of Fig. 8 is suitable for.

In addition, in the present embodiment, be provided with the desired location of fixed-site cylinder 30p is located at the slide-block mechanism that has rotated the position of 180 degree on the track that circles round of piston axis of rotation β ' that circles round from the position of clutch release slave cylinder running shaft γ, but, as described in when doing the explanation of expenditure as qualification, also can constitute the described slide-block mechanism (with reference to Figure 10) that limits mechanism as described piston rotation, this piston rotation limits mechanism on the track that circles round of piston axis of rotation β ' that circles round, and half the mobile steering channel 30g ' (with reference to Figure 10) of set angle of mobile position fixed cylinder 30p ' that moves the position beyond it and the move angle that has only rotated mobile position fixed cylinder 30p ' is set.For example, as shown in Figure 8, when being set at when fixed-site cylinder 30p rotated the position of 45 degree steering channel rotation 22.5 degree.At this moment, the explanation that expenditure is made in qualification as described as can be known, limiting as expenditure becomes identical (Figure 10 (5)) before the moving of the maximum moment and fixed-site cylinder.But by formula (9) as can be known, it is preceding littler than moving of fixed-site cylinder 30p that expenditure is made in its qualification.Thus, when reasons such as the load reduction qualification because of slide part diminishes as expenditure, or because of the restriction of component configuration etc. make fixed-site cylinder 30p be not arranged on the track that circles round of piston axis of rotation β ' that circles round when the position of clutch release slave cylinder running shaft γ has rotated the position of 180 degree, mobile position fixed cylinder 30p ' is set and mobile steering channel 30g ' gets final product.

Mode of execution in this explanation, near the piston axis of rotation β ' that circles round of the unusual rotation of the easy generation of the rotary work cylinder 30b that causes locking was immediate with clutch release slave cylinder running shaft γ, (when the piston axis of rotation β ' that circles round passes through clutch release slave cylinder running shaft γ) was prerequisite about equally the time with the offset Es of the radius of gyration Ep of the piston 30a that circles round and rotary work cylinder 30b.That is, do not consider the situation that radius of gyration Ep is different with offset Es.It is the reasons are as follows.

Radius of gyration Ep determines that by the offset Ec of pump eccentric part 6f1 and the bearing play offset of piston bearing hole 30a6 offset Es is determined by the offset Eb in the hole of the configuration rotary work cylinder 30b that is located at clutch release slave cylinder housing 30c3 and the peripheral part bearing play offset of clutch release slave cylinder housing 30c3.It is by making the track near the approaching piston axis of rotation β ' that circles round of clutch release slave cylinder running shaft γ pass through clutch release slave cylinder running shaft γ, being called the mechanism that changes the bearing offset forcibly and can change speech that the rotation of present embodiment limits mechanism.That is, the result who rotates qualification mechanism being set is that only near circle round piston axis of rotation β ' and clutch release slave cylinder running shaft γ were immediate, radius of gyration Ep equated with offset Es.

As described in above-mentioned paragraph, become and becomes big greatly by rotating the change limits the bearing offset that mechanism carries out difference, the load increase that qualification mechanism and pump eccentric part 6f1 apply, reliability reduction with offset Ec and offset Eb.Therefore, in the present embodiment, the gap of circle round piston 30a and pump groove 30g is made as 2 times of difference of offset Ec and offset Eb.Thus, near circle round piston axis of rotation β ' and clutch release slave cylinder running shaft γ are immediate, even radius of gyration Ep is different with offset Es, as shown in figure 22, the piston 30a that circles round is offset from the central shaft in the pump groove 30b1, but rotary work cylinder 30b is rotated unusually.Thus, do not need to change described bearing offset, put on the load that limits mechanism and pump eccentric part 6f1 and do not increase, have the effect that to guarantee reliability.

When the gap of will circle round piston 30a and pump groove 30g be made as offset Ec and offset Eb difference more than 2 times the time, the gap enlargement between piston 30a and the pump groove 30b1 of circling round, therefore, sealing reduces and performance reduces.Hence one can see that, the gap of circle round piston 30a and pump groove 30g is made as offset Ec and offset Eb difference below 2 times for well.

According to present embodiment, can suppress processing cost lower with simple key element shape, constitute the high pump chamber of seal simultaneously, therefore, in the positive displacement pump of low-cost and high performance rotary work cylinder formula, can structure of piston of enough clutch release slave cylinders avoid moving the danger of locking.Consequently, can realize being suitable for the positive displacement pump of small capacity.In addition, compare with the clutch release slave cylinder majorityization of conventional example, simple in structure and improved assembling performance, therefore can realize having reduced the positive displacement pump of processing cost.

(second mode of execution)

Then, use as Figure 12 of the enlarged elevation figure of fixed-site cylinder 30p with as Figure 13 of the transverse cross-sectional view of its L-L positive displacement pump that will the second mode of execution of the present invention scroll compressor 1 as oil feed pump 30 lift-launchs is described.This second mode of execution is different with first mode of execution at the point of the following stated, and other points are basic identical with first mode of execution, therefore omits repeat specification.

In this second mode of execution, by utilization be pressed into, bonding and electro-deposition constitutes fixed-site cylinder 30p to the centrepin 30P3 and the roller 30p4 cylindraceous of substrate 30c1 fixed configurations.Be provided with lip part 30p31 in the upper end of centrepin 30p3.Roller 30p4 is embedded in the main body projection 30p32 of centrepin 30P3, can not extract from centrepin 30p3 under the effect of lip part 30p31.In Figure 12, Figure 13, enlarge and drawn the diametric clearance of roller 30p4 and centrepin 30p3, but in fact, be below the 100 μ m.Thus, for the relative velocity that makes the strong position of sliding of roller 30p4 and steering channel 30g diminishes, roller 30p4 carries out rotation, therefore, sliding mode between fixed-site cylinder 30p and the steering channel 30g becomes good, and bad action such as vibration is suppressed, and plays the pump action effect more smoothly that makes oil feed pump 30.And then, can avoid the wearing and tearing of fixed-site cylinder 30p and steering channel 30g, because of blocking coming off of (こじり) caused fixed-site cylinder 30p etc., play the effect of the reliability that improves oil feed pump 30.

(the 3rd mode of execution)

Then, use describes as the scroll compressor 1 that oil feed pump 30 carries the positive displacement pump with third embodiment of the invention as Figure 14 of the suitable figure of L-L section of Figure 12.

In the 3rd mode of execution, identical with second mode of execution except that be provided with the slide roller 30p5 of roller tabular surface 30p51 at outer circumferential face, therefore omit explanation in addition.According to the 3rd mode of execution, the slide part area of slide roller 30p5 and steering channel 30g increases, and therefore, the danger of wearing and tearing reduces, and has the effect that can improve the high oil feed pump of reliability 30.

(the 4th mode of execution)

Below, use Figure 15, Figure 16 that the positive displacement pump with four embodiment of the invention is described as the scroll compressor 1 that oil feed pump 30 carries.

The 4th mode of execution is the axial position replacement framework 4 with bent axle 6, and is in the type that oil feed pump 30 sides are born, identical with first to the 3rd mode of execution in addition with oil feed pump 30 near the back pressure chamber 110.Therefore, the main use as the Figure 15 of the detailed enlarged view of (suitable with the N portion of Fig. 1) back pressure chamber near with as Figure 16 of the enlarged elevation figure of oil feed pump (suitable with the M portion of Fig. 1) describes, and omits the explanation beyond it.

In the 4th present embodiment, bent axle alar part 6h leaves (with reference to Figure 15) from framework 4, the cover (30c2 of Fig. 5) (with reference to Figure 16) on oil feed pump 30 tops of cancellation first to the 3rd mode of execution is rotated the end plate 30b4 supporting of clutch release slave cylinder 30b as the axle lower end surface 6z of the end of bent axle 6.The whole zone on the top of bent axle 6 is towards back pressure chamber 110, on the other hand, has in the bottom towards zone as the suction pressure of the inner space pressure of housing 8, so the inevitable effect downwards of pressing force.Thus, bent axle 6 is pushed end plate 30b4 downwards.Thus, can reduce following gap, that is, as the gap between the bottom surface of the upper surface of the piston 30a that circles round of the sideshake of oil feed pump 30 and pump groove 30b1, flat end 30a5 (lower surface of the piston that circles round) gap with gap, rotary work cylinder 30b and the substrate 30c1 upper surface of substrate 30c1 upper surface.Wherein, make minimum gap roughly become 0 and slide.Slide in which gap and to determine with the magnitude relationship of the thickness of the piston 30a that circles round by the degree of depth of pump groove 30b1.

When the thickness of the piston 30a that circles round than the degree of depth of pump groove 30b1 hour, slide in the gap of rotary work cylinder 30b and substrate 30c1 upper surface.At this moment, the action of the piston 30a that circles round of carrying out circumnutation is smooth, and therefore, the pump action with oil feed pump 30 integral body is effect more smoothly.On the contrary, when the thickness of the piston 30a that circles round was bigger than the degree of depth of pump groove 30b1, the gap between the bottom surface of circle round the top of piston 30a and pump groove 30b1, flat end 30a5 (lower surface of the piston that circles round) became slip surface with the gap of substrate 30c1 upper surface.At this moment, the gap at two positions can be suppressed therefore can further improve sealing, so have the effect that high performance oil feed pump is provided for minimum.

And then as shown in Figure 16, oil feed pump 30 integral body are fixed in the lower surface of the roller 25a that constitutes supplementary bearing 25 by pump set screw 30n.At this, the lower surface of roller 25a meets at right angles with respect to the inner peripheral surface as bearing surface.In addition, axle lower end surface 6z meets at right angles with respect to the central shaft of bent axle 6.Thus, no matter the lift-launch posture of bent axle 6 how, axle lower end surface 6z whole with end plate 30b4 butt, therefore, play the sealing that improves between axle lower end surface 6z and the end plate 30b4, the effect of high performance oil feed pump is provided.In addition, owing to suppressed the situation of the end in contact between axle lower end surface 6z and end plate 30b4, therefore, play the effect that the high oil feed pump of reliability can be provided.

Claims

1. positive displacement pump, it possesses:

Pump case, it has shell chamber;

The rotary work cylinder, it has the pump groove, and is configured to and can rotatablely moves in described shell chamber;

The piston that circles round, its gap is embedded in described pump groove and separates this pump groove, thereby forms two pump chambers,

Described circle round piston or described rotary work cylinder utilize driving source to carry out circumnutation or rotatablely move,

The rotary work cylinder can be that the center is rotated motion with the clutch release slave cylinder running shaft, and this clutch release slave cylinder running shaft is Es with respect to the offset of piston rotary shaft as the central shaft of the circumnutation of the piston that circles round,

Described pump groove intersects with clutch release slave cylinder running shaft as the central shaft that rotatablely moves of described rotary work cylinder and extends with straight line shape,

The described piston to-and-fro motion in described pump groove of circling round, and can carry out circumnutation ground with radius of gyration Ep with respect to described pump case and carry out spinning motion,

The radius of gyration Ep of the described piston that circles round and the offset Es of described rotary work cylinder about equally,

Described positive displacement pump is characterised in that,

The quantity that is embedded in the described piston that circles round of described rotary work cylinder is made as one,

Described positive displacement pump also has and rotate to limit mechanism, and this rotations qualification mechanism keeps the rotation of circling round of the described piston that circles round and described rotary work cylinder, and the speed of circling round of this piston that circles round is defined as 2 times of rotational speed of this rotary work cylinder.

2. positive displacement pump according to claim 1 is characterized in that,

Make expenditure less than making expenditure in circled round the qualification that described rotation during angle of circling round of 180 degree limits mechanism of described piston rotary shaft in the qualification of the described piston rotary shaft described rotation qualification mechanism during angle of circling round consistent with described clutch release slave cylinder running shaft.

3. positive displacement pump according to claim 1 and 2 is characterized in that,

By offset is the circumnutation that the bent axle of Ec is realized the described piston that circles round,

4. according to each described positive displacement pump in the claim 1～3, it is characterized in that,

Described rotation limits mechanism to be possessed: make the rotation of the described piston that circles round and the synchronous rotating synchro structure of rotation of described rotary work cylinder; The speed of circling round of the described piston that circles round is defined as 2 times piston rotation qualification mechanism of speed of autorotation.

5. positive displacement pump according to claim 4 is characterized in that,

Described rotating synchro structure constitutes by being provided with the par, side at the described piston that circles round, and the bi-side of this par, side and described pump groove are slidingly connected respectively.

6. according to claim 4 or 5 described positive displacement pumps, it is characterized in that,

Described piston rotation limits mechanism and possesses slide-block mechanism, this slide-block mechanism limits the motion of the described piston that circles round, make on the circumnutation track of the described piston axis of rotation that circles round, be in all the time by on the straight line on the described piston that circles round of described being fixed in of the piston axis of rotation of circling round with the rest point of described clutch release slave cylinder running shaft diverse location.

7. positive displacement pump according to claim 6 is characterized in that,

Described rest point is arranged at the position that the position from described clutch release slave cylinder running shaft on the described circumnutation track has rotated 180 degree.

8. according to claim 6 or 7 described positive displacement pumps, it is characterized in that,

Described slide-block mechanism possesses not movable slider and rotation guide,

9. positive displacement pump according to claim 8 is characterized in that,

Described not movable slider possesses: fixed center axis; Slider part, it inserts this fixed center axis and rotates freely.

10. according to Claim 8 or 9 described positive displacement pumps, it is characterized in that,

With the path of described steering channel as working fluid.

11. positive displacement pump according to claim 10 is characterized in that,

Described steering channel is extended to par, described side.

12. according to each described positive displacement pump in the claim 1～11, it is characterized in that,

Be equipped on described volume fluid machine as oily supply source from oil to the each several part of volume fluid machine that supply with.

13. a volume fluid machine possesses:

Driving source;

Bent axle by described driving source driving;

By the positive displacement pump of described crank-driven,

Described positive displacement pump possesses: pump case, and it has shell chamber; The rotary work cylinder, it has the pump groove and is configured to and can rotatablely move in described shell chamber; The piston that circles round, its gap is embedded in described pump groove and separates this pump groove, thereby forms two pump chambers,

Described circle round piston or described rotary work cylinder utilize described driving source to carry out circumnutation or rotatablely move,

The described piston that circles round moves back and forth in described pump groove, and can carry out circumnutation ground with radius of gyration Ep with respect to described pump case and carry out spinning motion,

Described volume fluid machine is characterised in that,

Described volume fluid machine also is provided with and rotate limits mechanism, and this rotations qualification mechanism keeps the rotation of circling round of the described piston that circles round and described rotary work cylinder, and the speed of circling round of this piston that circles round is defined as 2 times of rotational speed of this rotary work cylinder.