CN105980710A

CN105980710A - Pump device

Info

Publication number: CN105980710A
Application number: CN201580006836.5A
Authority: CN
Inventors: 川野裕司
Original assignee: Nippon Oil Pump Co Ltd
Current assignee: Nippon Oil Pump Co Ltd
Priority date: 2014-03-06
Filing date: 2015-02-25
Publication date: 2016-09-28
Also published as: TW201540955A; WO2015133342A1; JP2015169107A; EP3115608A4; EP3115608A1; US20170067463A1; KR20160132039A; JP6347478B2

Abstract

The purpose of the present invention is to suppress the occurrence of unevenness in a rotor of an internal gear pump, suppress the formation of gaps between the end surfaces (side surfaces) of an inner rotor and an outer rotor, and to prevent a decline in volume efficiency. Thus, the pump device of the present invention includes an internal gear pump (10), in which an inner rotor (13) is inscribed to an outer rotor (12), and includes a plate member (7) which is provided to an end surface of the rotors. The plate member (7) is formed of a material having high hardness, has a shape that does not block a suction port (150), has a through-hole (73) formed therein, and has O-ring grooves (71,72), which each have a continuous shape and house an O-ring, formed therein.

Description

Pump installation

Technical field

The present invention relates to a kind of crescent gear pump.

Background technology

There is external gear rotary pump and crescent gear pump (such as, Gerotor pump: registered trade mark) in gear pump.

In the past, with external gear rotary pump to comparing, use crescent gear pump in the region of relatively low pressure.

In recent years, propose to have coolant (coolant, cutting fluid) as the crescent gear pump of working fluid (for example, referring to patent documentation 1).

But, owing to there is harder impurity (particle) in coolant, therefore due to this harder impurity And the rotor abrasion of crescent gear pump.

And, when rotor weares and teares, the end face (side) at internal rotor with outer rotor forms gap, volume Efficiency can reduce, and produces the such problem of output reduction.

Then, at present, also it is not proposed for the effective countermeasure of the described problem of crescent gear pump.

Prior art literature

Patent documentation

Patent documentation 1: International Publication the 2012/053231st

Summary of the invention

The problem that invention is to be solved

The present invention proposes in view of above-mentioned problem of the prior art point, its object is to provide a kind of pump dress Put, it is possible to the abrasion to the rotor of crescent gear pump suppresses, suppress the end at internal rotor Yu outer rotor Face (side) forms gap, prevents volumetric efficiency from reducing.

For solving the means of problem

The pump installation (100～100C, 200～200C) of the present invention is characterised by, have internal rotor (13, 213) internal messing is in the crescent gear pump (10) of outer rotor (12,212), rotor (outer rotor 12, 212 and internal rotor 13,213) end face (suction side end face: with the source of driving away from the end face of side) It is provided with plate-shaped member (balance plate 7,7A, 207,207A), this plate-shaped member (balance plate 7,7A, 207,207A) it is made up of the material that hardness is higher, for not blocking the shape of suction inlet (150, Pi), shape Become and have through hole (discharge pressure entrance hole 73,73A), and be formed with continuous shape and house o-ring O-ring groove (71,71A, 72,72A, 207a, 207b, 207k, 207j).

Being preferably in the present invention, above-mentioned o-ring groove (71,72,207a, 207b) is formed at tabular Parts (balance plate 7,207) with rotor away from the face of side, o-ring has the magnitude of interference of regulation Be installed in the o-ring groove (71,72,207a, 207b) of regulation.

Or, be preferably in the present invention, plate-shaped member (balance plate 7A, 207A) with rotor phase Toss about and be formed with blind space (blind hole BH), in this blind space, house elastomeric element (9).

Be preferably in the present invention, rotor with above-mentioned plate-shaped member (balance plate 7,7A, 207,207A) Being configured with the second plate-shaped member (fixed plate 8) on the end face of opposition side, the second plate-shaped member (8) is not for seal Close the shape of tap (140).

Additionally, can also be in the present invention, the suction side of the working fluid of crescent gear pump and discharge side It is arranged in not homonymy relative to the rotary shaft direction of rotor.

Or, it is also possible to for, suction side and the discharge side of working fluid are joined relative to the rotary shaft direction of rotor Put in same side.

The effect of invention

According to possessing the present invention of above-mentioned composition, the end face at rotor (outer rotor and internal rotor) (sucks Side end face: with the source of driving away from the end face of side) on be provided with plate-shaped member (balance plate 7,7A, 207, 207A), this plate-shaped member (balance plate 7,7A, 207,207A) is made up of the material that hardness is higher, For not closing the shape of suction inlet (150, Pi), and be formed through hole (discharge pressure entrance hole 73, 73A), (arrange via gap and the through hole of outer rotor (12,212) with internal rotor (13,213) Go out pressure entrance hole 73,73A), to plate-shaped member (7,7A, 207,207A) with rotor away from one Side imports discharge pressure (or pressurized working fluid).

Here, be formed on plate-shaped member (balance plate 7,7A, 207,207A) o-ring groove (71, 71A, 72,72A, 207a, 207b, 207k, 207j), and chimeric have o-ring, therefore to plate-like portion Part (7,7A, 207,207A) imports discharge pressure, even if supplying pressurized working fluid, also leads to Cross o-ring to prevent from spilling.

Then, the area in the region being imported into discharge pressure of plate-shaped member (7,7A, 207,207A) It is set to, is made than the discharge pressure of outer rotor (12,212) Yu the gap of internal rotor (13,213) The area in region big, therefore plate-shaped member (7,7A, 207,207A) is by rotor-side (first Embodiment～the discharge side of the 4th embodiment: the left side of Fig. 1) pressing.

Even if discharge pressure becomes zero or negative pressure, due to by the magnitude of interference of o-ring, elastomeric element (bullet Spring 9) elastic reaction pressing, therefore rotor (12,13,212,213) and plate-shaped member (7, 7A, 207,207A) gap also it is formed without between.

According to the present invention, plate-shaped member (7,7A, 207,207A) is made up of the material that hardness is higher, Do not wear and tear.On the other hand, the flank wear of rotor (12,13,212,213), but owing to being pressed The plate-shaped member (7,7A, 207,207A) being pressed on this rotor does not weares and teares and keeps smooth state, because of The side of this rotor (12,13,212,213) will not be worn as concavo-convex.Then, relative to rotor (12, 13,212,213) amount worn and torn, plate-shaped member (7,7A, 207,207A) moves to this rotor-side, And less (being caused by abrasion) space (gap).The result that this space (gap) is reduced, for the present invention Pump installation for for volumetric efficiency improve.

Additionally, plate-shaped member (7,7A, 207,207A) becomes does not closes suction inlet (150, Pi) side Shape, hinder working fluid thus without owing to arranging plate-shaped member (7,7A, 207,207A) To the suction of crescent gear pump.

Here, the power pressed to rotor-side by plate-shaped member (7,7A, 207,207A) is from internal messing tooth The discharge pressure of wheel pump obtains, and therefore when the starting of crescent gear pump etc., discharge pressure does not act on plate Shape parts.

But, in the present invention, it is possible to by the mechanical power beyond the discharge pressure of crescent gear pump, Plate-shaped member (7,7A, 207,207A) is pressed to rotor-side.

Such as, o-ring is arranged in plate-shaped member (7,207) with rotor opposition side, o-ring has Have regulation the magnitude of interference be installed on o-ring groove (71,72,207a, 207b) in, the bullet of o-ring Property counter-force act on plate-shaped member (7,207), thus by plate-shaped member (7,207) to rotor-side press.

Or, plate-shaped member (7A, 207A) with the end face of rotor opposition side on to form blind space (blind Hole BH), in this blind space, house elastomeric element (9), the thus bullet of this elastomeric element (9: spring) Property counter-force acts on plate-shaped member (7A, 207A), and by plate-shaped member (7A, 207A) to rotor-side Pressing.

Thus, in the present invention, even if when the starting of crescent gear pump etc., plate-shaped member (7,7A, 207,207A) also pressed to rotor-side.

The plate-shaped member (7,7A, 207,207A) being made up of the material that hardness is higher as described above is no Wear and tear and keep smooth state, be therefore pressed against rotor thereon (12,13,212,213) side Will not wear and tear for concavo-convex in face.And, with the wear extent correspondingly tabular of rotor (12,13,212,213) Parts (7,7A, 207,207A) move to rotor-side and make (being caused by abrasion) space (gap) Reducing, therefore volumetric efficiency improves.

Accompanying drawing explanation

Fig. 1 is that the master of the first embodiment representing the present invention regards sectional view.

Fig. 2 is the side view of the rotor of the crescent gear pump of the first embodiment.

Fig. 3 is the figure of the balance plate representing the first embodiment.

Fig. 4 is to represent the partial cross section's front view near the balance plate of the first embodiment.

Fig. 5 is the figure of the fixed plate representing the first embodiment.

Fig. 6 is that the master representing second embodiment of the present invention regards sectional view.

Fig. 7 is that the master representing third embodiment of the present invention regards sectional view.

Fig. 8 is the figure of the balance plate representing the 3rd embodiment.

Fig. 9 is to represent the partial cross section's front view near the balance plate of the 3rd embodiment.

Figure 10 is that the master of the 4th embodiment representing the present invention regards sectional view.

Figure 11 is that the master of the 5th embodiment representing the present invention regards sectional view.

Figure 12 is the side view (the Y-direction view of Figure 11) representing the 5th embodiment.

Figure 13 is that the master of the 6th embodiment representing the present invention regards sectional view.

Figure 14 is that the master of the 7th embodiment representing the present invention regards sectional view.

Figure 15 is that the master of the 8th embodiment representing the present invention regards sectional view.

Detailed description of the invention

Hereinafter, with reference to add pay an accompanying drawing embodiments of the present invention are illustrated.

First, with reference to Fig. 1～Fig. 5, first embodiment of the present invention is illustrated.

In FIG, the overall pump installation represented by symbol 100 has crescent gear pump 10.

Crescent gear pump 10 partial gear case 11, outer rotor 12 and internal rotor 13.In FIG, Symbol 14 is pump case, and symbol 15 is pump lower end plate (hreinafter referred to as " end plate ").Internal rotor 13 schedule rotary shaft 5 by not shown keying.

Fig. 2 represents the state of the boosting of the working fluid engaging and producing due to outer rotor 12 and internal rotor 13.

In fig. 2, the crescent gear pump 10 of embodiment is, 7 internal tooth 12t of outer rotor 12 with 6 external tooth 13t engagements of internal rotor 13, and rotate (arrow R) to equidirectional.

By engaging of 6 external tooth 13t of 7 internal tooth 12t of outer rotor 12 and internal rotor 13, work Fluid is boosted.

In fig. 2, the working fluid of the region E1 being applied with hachure is boosted.

The working fluid of boosting in region E1 (Fig. 2), from the end face being formed at rotor 12,13 side Tap 140 (being illustrated by the broken lines in fig. 2), via the discharge duct 141 of pump case 14 (Fig. 1), Discharge from outlet 142.

In FIG, pump installation 100 is, is provided with a cyclone 40 on cyclone shell 45, The radial outside of cyclone 40 is provided with multiple swirl flow device 50.Cyclone 40 and secondary Cyclone 50 is the taper parts of lower end (impurity outlet 42,52) undergauge.At cyclone shell 45 Lower end, be formed with the inflow entrance 45i for being taken into working fluid.

Further, pump installation 100 has impeller 30 (the cyclone relaying leaf being housed within impeller housing 31 Wheel).

It is configured with taper guide member 55 in the lower section of a cyclone 40, is provided with miscellaneous in lower section further Matter is discharged with impeller 60.

Internal rotor 13, cyclone relaying impeller 30, impurity discharge impeller 60 are fixed on rotary shaft 5, and Rotated by not shown electro-motor and drive.

Flowing (F1～F11:Fc1～Fc4) to the working fluid being taken into from the inflow entrance 45i of pump installation 100 Illustrate.

The working fluid F1 being taken into from inflow entrance 45i rises (arrow F2) in cyclone shell 45, Turn back and flow into (arrow F3) to a cyclone 40 in the top of guide member 312.

Working fluid to cyclone 40 inflow declines (arrow F4) along rotary shaft 5 with eddy current shape, The impurity (impurity such as cutting powder that such as, coolant is comprised) that proportion is bigger is from impurity outlet 42 row Going out (the arrow Fc1 being illustrated by the broken lines), the working fluid of cleaning rises to the position of cyclone relaying impeller 30 Put (arrow F5).

By the rotation of cyclone relaying impeller 30, working fluid is boosted and flows in 2 impellers 50 (arrow F6).

The working fluid flowed into swirl flow device 50 declines (arrow F7) with eddy current shape, and proportion is bigger Impurity declines and discharges from impurity outlet 52, (is illustrated by the broken lines along taper guide member 55 landing Arrow Fc2), by two stages the working fluid that cleans rise and in the suction being arranged at intake panel 20 (arrow F8) is flow through in pipe 21.

Working fluid passes through in the stream 22 of intake panel 20, inwardly nibbles from the suction inlet 150 of end plate 15 Close the internal suction (arrow F9) of gear pump 10.How, boosted by crescent gear pump 10, via The tap 140 of pump case 14, discharge duct 141, discharge (arrow from the outlet 142 of pump case 14 Head F10, arrow F11).In detail by aftermentioned, but the working fluid boosted by crescent gear pump 10 A part (being represented by arrow F10R), to the discharge pressure entrance hole 73 (Fig. 3) being formed at balance plate 7 Interior inflow.

Additionally, discharge from the impurity outlet 42 of a cyclone 40 and the impurity of swirl flow device 50 The working fluids (arrow Fc1, Fc2) comprising impurity that mouth 52 is discharged, by impurity discharge impeller 60 Give dynamic pressure (arrow Fc3), to pump, discharge (arrow Fc4) from impurity outlet 63.

Pump installation 100 shown in Fig. 1, is the direction (figure of the rotary shaft 5 relative to crescent gear pump 10 Above-below direction in 1), the suction side (end plate 15 side) of working fluid and discharge side (pump case 14 side) It is arranged in the pump of the not type of homonymy.

The empirical law grasped as inventor, in the pump installation of described type, crescent gear pump The rotor 12,13 of 10, produces end plate 15 side (suction side: be lower section in FIG) than pump case 14 The abrasion big phenomenon of quantitative change of side (discharge side: be top in FIG).

In order to suppress the ladder produced due to the described abrasion of rotor 12,13 poor, at pump installation 100 In gear pump 10, it is configured with balance plate 7 (ginseng in end plate 15 side (suction side: in FIG for downside) According to Fig. 3).Balance plate 7 is made up of the material that hardness is higher.

In FIG, the face 15f connected with rotor 12,13 of end plate 15 is formed with balance plate to install Hole 15h, the depth dimensions of balance plate installing hole 15h is more slightly larger than the gauge of balance plate 7.And, flat Weighing apparatus plate 7 is installed on balance plate installing hole 15h.

As it is shown on figure 3, balance plate 7 have make radius different two semicircle 7oa (bigger semicircle), Base mutual for 7ob (less semicircle) connects such flat shape.

In the part that semicircle 7oa, 7ob are connected, semicircle 7oa, 7ob are via the less circular arc of radial dimension R and connect swimmingly.

In figure 3, the center of curvature of bigger semicircle 7oa is represented by symbol C1, less semicircle 7ob The center of curvature represented by symbol C2.In figure 3, two centers of curvature C1, C2 are (in figure 3 On above-below direction) biasing.

Being formed with type annular groove 71,72 in the plane of balance plate 7, o-ring groove 71,72 plane earth is formed For circular, its cross sectional shape is rectangle.

The center C3 of the o-ring groove 72 of (radial dimension) less side, is positioned at by above-mentioned curvature In horizontal line L h (chain-dotted line extended along left and right directions in figure 3) of heart C1, and it is located relative to The position that center of curvature C1 biases the most to the left.

Radially inner side at less o-ring groove 72 is formed with through hole 7i.Through hole 7i and o-ring With one heart, the radius of through hole 7i is less than the radius of curvature of less o-ring groove 72 for groove 72.And, Through hole 7i is inserted with rotary shaft 5 (Fig. 1).

In Fig. 1, Fig. 3, omit diagram, but be embedded in o-ring (relatively at o-ring groove 71,72 In the working fluid indefatigable elastomeric element of tool: such as rubber system).

In the bottom of balance plate installing hole 15h (with reference to Fig. 1), the two o-ring illustrated by omission, The region E2 surrounded by two o-ring grooves 71,72 shown in Fig. 3 (is applied with the district of hachure in Fig. 3 Territory) become the space (sealing space) sealed.

In this sealing space (in Fig. 3, by the region E2 of o-ring groove 71,72 encirclement: in figure 3 It is applied with the region of hachure) in, it is formed with the passing through of 2 positions that the thickness direction along balance plate 7 extends Through hole (discharge pressure entrance hole) 73, working fluid (working fluid represented by arrow F10R) via Through hole 73 invades.The work invaded to above-mentioned sealing space (being applied with the region E2 of hachure in Fig. 3) Fluid, additional make balance plate 7 above Fig. 1 movement by pressure, and by balance plate 7 to rotor 12, 13 pressings.

Additionally, the discharge pressure entrance hole 73 of the 2 of balance plate 7 positions is configured to, though side's quilt Internal rotor 13 blocks, and the opposing party is also not plugged up.

Symbol 74 in Fig. 3, for the pin-and-hole for inserting not shown spline pin.Stopped by not shown Ship and resell on another market, prevent balance plate 7 from rotating (being caused being rotated by the rotation of rotary shaft 5).

Additionally, pin-and-hole 74 is blind hole, to being formed with o-ring groove 71,72 1 side opening.

In FIG, in the upside (with balance plate 7 opposition side) of rotor 12,13, with rotor 12, 13 modes connected are configured with fixed plate 8.Fixed plate 8 is higher by the hardness of hardness ratio rotor 12,13 Material is constituted.Further, preferred hardness is higher than the hardness of the impurity likely mixed in coolant.

Fig. 5 represents the details of this fixed plate 8.

In Figure 5, fixed plate 8 is formed with suction inlet 82 and tap 81.But it is also possible to It is formed without the suction inlet 82 of fixed plate 8.Additionally, in the case of not forming the suction inlet 82 of fixed plate 8, Seal pressure escape orifice (not shown) to need to connect with suction chamber.

The fixed plate (fixed plate of the first embodiment) 8 of Fig. 5 only illustrates following situation: in order to realize with Suction side and the discharge side of working fluid are arranged in the type of same side relative to the rotary shaft direction of internal rotor The sharing (sharings of parts) of fixed plate of pump (Figure 11～Figure 15), and define suction inlet 82 and the both sides of tap 81.Here, in the case of direction of rotation difference, by pump (Figure 11～figure 15) fixed plate turns over use.

The installing hole shipped and resell on another market till symbol 84 in Fig. 5, symbol 8i is the insertion hole of rotary shaft 5.

In crescent gear pump 10, the gap of outer rotor 12 and internal rotor 13 be from suction side (Fig. 1's Downside) continue to discharge side (upside of Fig. 1).Therefore, the discharge pressure of crescent gear pump 10 is at pump On rotary shaft direction (above-below direction of Fig. 1), via the gap (arrow of outer rotor 12 with internal rotor 13 F10R) and be formed at the discharge pressure entrance hole 73 of balance plate 7, import in Fig. 1 of balance plate 7 Lower surface (bottom of balance plate installing hole 15h), and (Fig. 3 is applied with shadow to above-mentioned sealing space The region E2 of line) supply (applying).Then, by balance plate 7 to rotor 12,13 (upper to Fig. 1 Side) pressing.

On the other hand, in fig. 2, be applied with the region E1 of hachure be certain moment outer rotor 12 with The gap of internal rotor 13, represents the region that discharge pressure is acted on.Then, the region E1 of hachure it is applied with Discharge pressure act as, by lower section from balance plate 7 to Fig. 1 (from rotor 12,13 away from direction) Pressing.

As according to knowable to Fig. 2, Fig. 3, it is set as:

The area of the area ＜ E2 of E1

Therefore the pressure applied the E2 side (downside of the balance plate 7 in Fig. 1) that area is bigger, is better than The pressure that the E1 side (upside of the balance plate 7 in Fig. 1) that area is less is applied.As its result, Balance plate 7 is pressed to discharge side (upside of Fig. 1: rotor 12,13 side).

Here, when by balance plate 7 when the power that discharge side (upside of Fig. 1) presses is too strong, to region The pressure that E2 side applies can hinder the rotation of rotor 12,13.On the other hand, when by balance plate 7 to rotor 12, when the power that 13 sides (upside of Fig. 1) presses is crossed weak, due to rotor 12,13 end abrasion and Volumetric efficiency can reduce.

In the first embodiment, in the way of not producing described problem, determine position (that is, the O of o-ring The position of type annular groove 71,72).In other words, the position of o-ring groove 71,72 is set to following location: The pressure applying E2 side, region will not hinder the rotation of rotor 12,13, and, balance plate 7 is by turning Son 12,13 sides (upside of Fig. 1) reliably presses, it is possible to prevent the mill of end by rotor 12,13 Damage causes volumetric efficiency to reduce.

Additionally, in real machine, due to by from E1 outer rotor via 12 periphery, region and internal rotor 13 inner circumferential The impact of the barometric gradient of the discharge pressure spilt, therefore the area of region E2 is determined by experiment.

In figure 3, two o-ring grooves 71,72 the region E2 surrounded is set to, suction inlet (figure Being represented the region of boundary line by dotted line Li in 3) side (downside of Fig. 3) is minimum, tap 140 (Fig. 3 In the region Lo that surrounded by double dot dash line) side is bigger.Pump discharge head and suction pressure are in a ratio of high pressure, Therefore the pump discharge side region Lo discharge pressure of balance plate 7 acted on bigger pressure to rotor 12, 13 side pressings.That is, two o-ring grooves 71,72 are set to, in balance plate 7, by discharge pressure The region acted on i.e. pump discharge side region Lo, makes to put down with bigger pressure pressing to rotor 12,13 side Weighing apparatus plate 7 presses the amount of rotor 12,13 becomes impartial.

On the other hand, balance plate 7 becomes the shape do not closed by suction inlet 150 (the symbol Li in Fig. 3) side seal Shape, for hindering the shape sucking working fluid to crescent gear pump 10.In other words, in suction side (downside in Fig. 1), is not balanced the suction inlet 150 of the region composition crescent gear pump 10 that plate 7 is closed.

The balance plate 7 with described structure is, by the discharge pressure of crescent gear pump 10, by rotor 12, suction side (downside of Fig. 1) end face of 13 presses to discharge side (upside of Fig. 1).

As described above, balance plate 7 is made up of the material that hardness is higher, keeps smooth thus without abrasion State.Therefore, will not wear and tear for concavo-convex in the side of the rotor 12,13 pressing on balance plate 7.Then, Corresponding with the amount of rotor 12,13 abrasion, balance plate 7, to rotor 12,13 side shifting, reduces by wearing and tearing The space (gap) caused.Therefore, the volumetric efficiency of crescent gear pump 10 improves.

As described above, balance plate 7 is pressed to suction side (downside of Fig. 1) end face of rotor 12,13 The power of pressure, obtains from the discharge pressure of crescent gear pump 10.Therefore, rising at crescent gear pump 10 Time dynamic, discharge pressure does not act on balance plate.

On the other hand, in the first embodiment, deep than o-ring groove 71,72 of the diameter dimension in cross section The o-ring that degree size is big is installed in o-ring groove 71,72, the most as shown in Figure 4, and o-ring The elastic reaction Fr of OR is to o-ring groove 71,72 reduction effect, by this elastic reaction Fr (at Fig. 4 In upward effect), balance plate 7 is pressed against the lower end of rotor 12,13 (omitting diagram in the diagram) Face.

In other words, in the first embodiment, such as when starting balance plate 7 pressed on rotor 12, The initial pressure of the lower surface of 13, is obtained by the elastic reaction Fr of o-ring.Therefore, though including When the discharge pressure of intermeshing gear pump 10 does not act on the starting of balance plate 7, balance plate 7 is also pressed against Lower surface in Fig. 4 of rotor 12,13.Here, the balance plate 7 being made up of the material that hardness is higher is not Wearing and tearing and keep smooth state, will not wear and tear in the side of the rotor 12,13 therefore pressing on balance plate 7 For concavo-convex, it is poor that the side of suppression rotor 12,13 forms ladder.Then, wear and tear with rotor 12,13 divides Corresponding, balance plate 7 reduces the space (gap) caused by abrasion to rotor 12,13 side shifting.Make For its result, the volumetric efficiency of crescent gear pump 10 improves.

Then, with reference to Fig. 6, second embodiment of the present invention is reduced explanation.In figure 6, pump installation Entirety is represented by symbol 100A.

In the first embodiment shown in Fig. 1～Fig. 5, the discharge side of crescent gear pump 10 is (at Fig. 1 In for the top of rotor 12,13) be provided with fixed plate 8 (Fig. 5).

On the other hand, in second embodiment of Fig. 6, it is not provided with fixed plate.Experiment according to inventor is sentenced Bright: in rotor 12,13, pump case 14 side (discharge side: be the upper of rotor 12,13 in figure 6 Abrasion just) is little.Therefore, the difference of specification as requested, it is possible to omit fixed plate.

Other compositions, action effect and first embodiment of Fig. 1～Fig. 5 of second embodiment of Fig. 6 Equally.

With reference to Fig. 7～Fig. 9, third embodiment of the present invention is illustrated.In the figure 7, pump installation Entirety is represented by symbol 100B.

In first embodiment and the second embodiment of Fig. 1～Fig. 6, as shown in Figure 4, exist During the starting of crescent gear pump 10, by balance plate 7 to discharge side (upside in Fig. 1) press initial The pressure ((power such as when starting, balance plate 7 pressed to the end face of rotor 12,13: towards Fig. 4 The power of top), obtained by the elastic reaction Fr of o-ring.

On the other hand, in the 3rd embodiment of Fig. 7～Fig. 9, not by the elastic reaction of o-ring, And by the elastic reaction of spring (helical spring) 9, when the starting of crescent gear pump 10, obtain The initial pressure pressed to discharge side (in Fig. 7 upside) by balance plate 7A is (by balance plate 7A to rotor 12, the power of the end face pressing of 13: power the most upward).

As Fig. 9 Yu Fig. 4 is compared and can clearly as, in the third embodiment, balance plate O-ring groove 71A, 72A or the position (with reference to Fig. 9) of o-ring OR on 7A are implemented with first Mode, the second embodiment (with reference to Fig. 4) are different.

In Fig. 4 (the first embodiment, the second embodiment), o-ring groove 71 on balance plate 7, 72 or o-ring OR be formed on suction side (lower section of Fig. 4) end face of balance plate 7.

On the other hand, in Fig. 9 (the 3rd embodiment), o-ring groove 71A on balance plate 7A, 72A or o-ring OR are, relative to rotary shaft direction (above-below direction of Fig. 9), to be arranged in balance Region between suction side (lower section of Fig. 9) end face and discharge side (top of Fig. 9) end face of plate 7A In and on the position along the outer peripheral face of balance plate 7A and inner peripheral surface.And, inner side o-ring 72A is facing with the lining BS being fitted and fixed with in end plate 15.

As shown in Fig. 9 (and Fig. 7), on suction side (downside of Fig. 7) end face of balance plate 7A It is formed with blind hole BH, in this blind hole BH, contains spring 9.This spring 9 is received with the state compressed Holding, spring 9 is to the direction of elongation effect elastic reaction.

As its result, by the elastic reaction (power of spring 9 elongation) of spring 9, balance plate 7A quilt To discharge side (upside in Fig. 7, Fig. 9) pressing, obtain initial pressure when crescent gear pump 10 starts Power (power such as when starting, balance plate 7A pressed to the end face of rotor 12,13).

In fig. 8, symbol 73A represents that discharge pressure entrance hole 73, symbol 74A represent the peace of spline pin Dress hole.

Additionally, the circle (chain-dotted line) represented by symbol G at the two ends, left and right of Fig. 8, represent and be arranged at balance The abutted position of 2 springs 9 of plate installing hole 15h.

Additionally, the fixed plate of the 3rd embodiment uses the fixed plate 8 common with the first embodiment.

By the elastic reaction of spring 9 obtain crescent gear pump start time initial pressure the 3rd In embodiment, with obtained by the elastic reaction of o-ring initial pressure the first embodiment and Second embodiment compares, it is possible to will be set by the amount (amount of movement) of elastic reaction pressing balance plate 7A Fixed bigger than the first embodiment, the second embodiment.

Therefore, in the third embodiment, even if the abrasion quantitative change of rotor 12,13 is big, higher by hardness Material constitute and do not wear and tear and keep the balance plate 7A of flat condition by the side to rotor 12,13 Suitably press.Therefore, suppression is poor at the side of rotor 12,13 formation ladder.Then, with rotor 12, The amounts of 13 abrasions are corresponding, space that balance plate 7 makes to rotor 12,13 side shifting to be caused by abrasion ( Gap) reduce, therefore volumetric efficiency improves.

Other of 3rd embodiment of Fig. 7～Fig. 9 are constituted and the enforcement of action effect and Fig. 1～Fig. 6 Mode is same.

Then, with reference to Figure 10, the 4th embodiment of the present invention is illustrated.In Fig. 10, pump installation Entirety represented by symbol 100C.

In the 3rd embodiment of Fig. 7～Fig. 9, in the discharge side (upside in Fig. 7) of crescent gear pump It is provided with fixed plate 8 (as Fig. 5).On the other hand, it is not provided with in the 4th embodiment of Figure 10 Fixed plate.

Other compositions, action effect and the 3rd embodiment party of Fig. 7～Fig. 9 of the 4th embodiment of Figure 10 Formula is same.

It follows that the 5th embodiment of the present invention is illustrated with reference to Figure 11～Figure 14.At Figure 11 In, the entirety of pump installation is represented by symbol 200.

First embodiment of Fig. 1～Figure 10～the 4th embodiment, be all the suction being applied to working fluid Enter side and discharge side and be arranged in the pump installation of the not type of homonymy relative to the rotary shaft direction of internal rotor 13 Embodiment.

On the other hand, in the 5th embodiment of Figure 11～Figure 14, it it is the suction being applied to working fluid Side and discharge side are arranged in the pump installation of the type of same side relative to the rotary shaft direction of internal rotor 213 Embodiment.

In Figure 11 and Figure 12, the overall pump installation represented by symbol 200 has rotary shaft 205, tooth Roller box 211, outer rotor 212, internal rotor 213, pump case 214, end cap 215 and support member 216. Support member 216, pump case 214, gear-box 211 and end cap 215, by 2 in-and-out bolt B1 It is fixed as 1 body with nut with gasket NW.And, support member 216 and pump case 214 are passed through Bolt B 2 fastens, and end cap 215, gear-box 211 and pump case 214 are fastened by bolt B 3.

The through pump case of rotary shaft 205 214, internal rotor 213, and by being clipped on the bearing of pump case 214 BG and be clipped on the bearing BS of end cap 215 and carry out axle and support.

Here, symbol K represents that the key that internal rotor 213 is fixed on rotary shaft 205, symbol SW represent Thrust washer, symbol M S represents oil sealing.

In fig. 11, (end cap 215 in Figure 11, face of the side that connects with rotor 212,213 of end cap 215 Left side) on, be formed with balance plate installing hole (blind hole) 215H for installing balance plate 207.

On the other hand, the face (pump case in Figure 11 of the side that connects with rotor 212,213 of pump case 214 The right side of 214) on, it is formed with fixed plate installing hole (recess) 214H for mounting plate 8.

In fig. 12, working fluid is, sucks to pump installation 200 as shown in hollow arrow Fi, as Flow through in pump installation 200 as shown in the arrow of dotted line, from pump installation as shown in hollow arrow Fo 200 discharge.

In fig. 12, symbol Pi represents that suction inlet, symbol Po represent tap.As shown in Figure 13, In the 5th embodiment, relative to rotary shaft direction, suction inlet Pi and tap Po is present in same side. Therefore, in fig. 12, it is in the situation of same side as suction inlet Pi and tap Po, and illustrates double Side.

At Figure 11, Tu12Zhong, outer rotor 212, internal rotor 213 rotate to equidirectional, from suction inlet The working fluid that Pi flows into is boosted by the volume variation in the gap between the gear of rotor 212,213, And discharge to pump installation 200 from outlet 214o of pump case 214 (Figure 12) via tap Po.

The structure of the balance plate 207 (Figure 11) in pump installation 200 and the balance plate 7 in the first embodiment (Fig. 3) structure is common.But, owing to the direction of rotation of rotor is different, therefore balance plate 207 is relative Balance plate in Fig. 3 becomes the shape of the X-X axisymmetrical about Fig. 3.

Balance plate 207 has the bigger o-ring groove 207a of radius size and the less o-ring of radial dimension Groove 207b, chimeric respectively in o-ring groove 207a, 207b have o-ring.And, at balance plate 207 On be perforated with through hole (as the discharge pressure entrance hole 73 of Fig. 3), and be perforated with the pin-and-hole of spline (as the pin-and-hole 74 of Fig. 3).

The fixed plate 8 of the 5th embodiment is also the structure common with the fixed plate 8 of the first embodiment.But It is that, in the case of rotor direction of rotation difference, the fixed plate 8 of the 5th embodiment becomes to be implemented first The upturned structure of fixed plate 8 of mode.

In the 5th embodiment of Figure 11, Figure 12, also as first embodiment of Fig. 1～Fig. 5, Balance plate 207 is pressed against rotor 212,213.Then, the initial pressure elastic reaction by o-ring Obtain.

Other of 5th embodiment of Figure 11, Figure 12 are constituted and the of action effect and Fig. 1～Fig. 5 One embodiment is same.

Then, with reference to Figure 13, the 6th embodiment of the present invention is illustrated.In fig. 13, pump installation Entirety represented by symbol 200A.

The 5th embodiment at Figure 11, Figure 12 is opened, relative to the rotary shaft direction of crescent gear pump, It is provided with fixed plate 8 driving source (left side in Figure 11).

On the other hand, in the 6th embodiment of Figure 13, it is not provided with fixed plate.

Other compositions of 6th embodiment of Figure 13, action effect are implemented with the 5th of Figure 11, Figure 12 5th embodiment of mode is same.

Then, with reference to Figure 14, the 7th embodiment is illustrated.In fig. 14, the entirety of pump installation by Symbol 200B represents.

In Figure 11～Figure 13, when the starting of crescent gear pump etc., discharge pressure do not act on balance In the case of plate 207, by balance plate 207 to the initial pressure driving source (left side in Figure 11) to press, As the first embodiment and the second embodiment, obtained by the elastic reaction of o-ring.

On the other hand, in the 7th embodiment of Figure 14, when the starting of crescent gear pump etc., row Go out in the case of pressure do not acts on balance plate 207A, by balance plate 207A to driving source (in Figure 14 Left side) initial pressure that presses, as the 3rd embodiment and the 4th embodiment, passes through spring The elastic reaction of 209 obtains.

The structure of the balance plate 207A (Figure 14) of pump installation 200B and the balance plate 7A of the 3rd embodiment The structure of (Fig. 8, Fig. 9) is common.But, owing to the direction of rotation of rotor is different, therefore balance plate 207A Balance plate 7A relative to Fig. 8 becomes the shape of the X-X axisymmetrical about Fig. 8.

Then, in pump installation 200B, even if the abrasion quantitative change of rotor 212,213 is big, by hardness relatively High material constitutes and does not weares and teares and keep the balance plate 207A of flat condition by rotor 212,213 Side suitably press, therefore suppression rotor 212,213 side produce ladder poor.Then, with turn The amount of son 212,213 abrasion is corresponding, and balance plate 207A makes by grinding to rotor 212,213 side shifting Damaging the space (gap) caused to reduce, therefore volumetric efficiency improves.

Other of 7th embodiment of Figure 14 are constituted and the embodiment party of action effect and Figure 11～Figure 13 Formula is same.

Then, with reference to Figure 15, the 8th embodiment of the present invention is illustrated.In fig .15, pump installation Entirety represented by symbol 200C.

In the 7th embodiment of Figure 14, relative to rotary shaft direction, driving source (in Figure 14 left Side) it is provided with fixed plate 8.

On the other hand, in the 8th embodiment of Figure 15, it is not provided with fixed plate.

Other composition, action effects of 8th embodiment of Figure 15 are as the 7th embodiment of Figure 14.

Embodiment illustrated is only and illustrates, and is not the record with the technical scope limiting the present invention as purport.

Such as, in the illustrated embodiment, balance plate is provided only on suction side (right side in Fig. 1), not It is arranged on discharge side (left side in Fig. 1).On the other hand, it is also possible to balance plate is provided only on discharge side (figure Left side in 1).In this case, need to change relative to the shape of embodiment illustrated boil on the nape opposite the mouth.

The explanation of symbol

5 rotary shafts

7 balance plates

8 fixed plates

9 springs

10 crescent gear pumps

11 gear-boxes

12 outer rotors

13 internal rotors

14 pump case

15 end plates

20 intake panels

30 cyclone relaying impellers

No. 40 cyclones

45 cyclone shells

50 swirl flow devices

60 impurity discharge impellers

Claims

1. a pump installation, it is characterised in that

There is internal rotor internal messing in the crescent gear pump of outer rotor, the end face of rotor arranges plate-like portion Part, this plate-shaped member is made up of the material that hardness is higher, for not closing the shape of suction inlet, is formed through Hole, and be formed with continuous shape and house the o-ring groove of o-ring.

2. pump installation as claimed in claim 1, wherein,

Above-mentioned o-ring groove be formed at plate-shaped member with rotor away from the face of side, o-ring is with regulation The magnitude of interference be installed in o-ring groove.

3. pump installation as claimed in claim 1, wherein,

It is formed with blind space at plate-shaped member with rotor opposition side, in this blind space, houses elastomeric element.