CN102914338A - High-pressure resistant two-way cycloid rotameter - Google Patents
High-pressure resistant two-way cycloid rotameter Download PDFInfo
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- CN102914338A CN102914338A CN2012104527170A CN201210452717A CN102914338A CN 102914338 A CN102914338 A CN 102914338A CN 2012104527170 A CN2012104527170 A CN 2012104527170A CN 201210452717 A CN201210452717 A CN 201210452717A CN 102914338 A CN102914338 A CN 102914338A
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Abstract
The invention discloses a high-pressure resistant two-way cycloid rotameter which adopts the structure that an upper end cover, a ring-shaped hollow housing and a lower end cover form a high-pressure resistant closing cavity with a built-in gear shaft which is rested in shaft holes on the upper end cover and the lower end cover respectively; a cycloid type inner rotor is mounted on the gear shaft and is connected with the gear shaft through a high-precision ball bearing or an oilless bearing; an outer rotor is arranged outside and meshed with the inner rotor; the oilless bearing fixed on the ring-shaped hollow housing is arranged on the outer side of the outer rotor; the outer rotor can freely rotate in the oilless bearing; the rotary shaft center of the inner rotor and that of an outer rotor are eccentric, and the eccentricity is e; a plurality of pairs of magnetic steels are respectively arranged on the upper end surface of the outer rotor and center the rotary shaft of the outer rotor, and the magnetic steels are in pairs, and the N poles and the S poles are arranged at intervals; two small holes are formed on the upper end cover and center the rotary shaft of the outer rotor; and two high-pressure resistant non-magnetic-conductive isolating pieces are respectively mounted at the lower ends of the two small holes, and each isolating piece is provided with a magnetic-sensing sensor.
Description
Technical field
The present invention relates to a kind of liquid capacity formula flowmeter, particularly a kind of high voltage-resistant bi-directional cycloid rotor flowmeter.
Background technology
Flow instrumentation occupies larger proportion in all multi-parameter detector tables in the fields such as process industry, public utilities and accumulating handing-over.Volumeter is widely used at industrial control field because precision is high, be not subjected to the pipeline mounting condition to limit, can be used for the advantages such as high viscosity liquid is measured, measurement range is wide.Traditional with the volumeter of gear as transmission body, mostly be the noncircular gear flowmeter, such as oval gear flowmeter, Roots-type flow meter etc.Wherein Roots-type flow meter is because can't from engagement, need to add the auxiliary engagement of gear, so can not make high voltage bearing structure.Patent of invention CN1828233A " high voltage-resistant bi-directional elliptic gear flow meter " discloses a kind of bi-directional elliptic gear flow meter, on an elliptic gear end face N utmost point two magnet steel extremely opposite with S that become 180 ° of layouts centered by gear shaft is installed therein; And in upper end cover, have 90 ° of layouts of one-tenth Hall elements centered by same gear shaft, but utilize the two-way flow of the phase differential test fluid of two sensors output pulses.But elliptic gear complex structure, processing difficulties, processing cost height and precision are difficult to guarantee, and disclosed high voltage-resistant bi-directional elliptic gear flow meter can only be arranged a pair of magnet steel among the invention CN1828233A, and resolution is lower.
Have in the market high voltage bearing Cylindrical Gear Meter, the VS Series Gear flowmeter of producing such as German Wei Shi company, adopt a pair of intermeshing cylindrical gear to do transmission body, and in upper end cover, arrange permanent magnet and Hall element with detection rotor rotational displacement signal metered flow, resolution is very high.But its shortcoming is when larger by flow, rotor speed is very high, the fluid pressure loss that causes thus is larger, and because flowmeter high and low pressure side pressure reduction is larger, gear is subjected to radial imbalance force larger, the High precise ball bear that be used for to connect gear rotor and gear shaft easy wear out failure when high rotating speed and under the effect of uneven radial force.
Summary of the invention
The technical matters that the present invention will approach provides and a kind ofly is easy to process and the high voltage-resistant bi-directional cycloid rotor flowmeter of long service life.
In order to solve the problems of the technologies described above, the invention provides a kind of high voltage-resistant bi-directional cycloid rotor flowmeter, comprise by upper end cover, toroidal cavity housing and bottom end cover and form high pressure resistant closed cavity, be respectively equipped with gear shaft, intermeshing internal rotor and outer rotor in the toroidal cavity housing, the up and down two ends of gear shaft rely on transition fit to realize linking to each other with upper end cover and bottom end cover respectively; Gear shaft is sleeved in the inner chamber of internal rotor, and internal rotor is sleeved in the inner chamber of outer rotor, and internal rotor is rotatedly connected by bearing I and gear shaft, and outer rotor is rotatedly connected by bearing II and toroidal cavity housing;
The revolution axle center of outer rotor and the revolving shaft of internal rotor are felt in off-centre, and the internal rotor outer wall that rotates in the inner chamber of outer rotor and outer rotor inwall form the annular seal space of several volume cycle variation;
At the permanent-magnet steel assembly that arranges 1 ~ 4 pair on the upper surface of outer rotor centered by the outer rotor revolving shaft, every pair of permanent-magnet steel assembly becomes the permanent-magnet steel of 180 ° of layouts to form centered by the outer rotor revolving shaft by two; The N utmost point and the S that are positioned at the adjacent permanent-magnet steel on the outer rotor stagger extremely mutually;
First sensor aperture and the second sensor aperture are set in upper end cover, first sensor aperture and the second sensor aperture all run through upper end cover, be provided with separately high pressure resistant, a non-magnetic spacer in first sensor aperture and the second sensor aperture, arrange one piece of magneto-dependent sensor on the every spacer;
Be provided with oil storage tank I and oil storage tank II at bottom end cover, connect the internal rotor revolving shaft at the subpoint of bottom end cover and outer rotor revolving shaft at the subpoint of bottom end cover as the eccentric throw line; Oil storage tank I and oil storage tank II lay respectively at the both sides of eccentric throw line; Internal rotor outer wall and outer rotor inwall form annular seal space that several volume cycle changes and are connected with in oil storage tank I and the oil storage tank II any one;
Be respectively equipped with logical hydraulic fluid port I and logical hydraulic fluid port II at bottom end cover, logical hydraulic fluid port I is connected with the oil storage tank I, and logical hydraulic fluid port II is connected with the oil storage tank II;
Be provided with and oil storage tank I and oil storage tank II mutually one to one all pressure oil groove I and all pressure oil groove II at upper end cover, thereby guarantee the axially loaded balance of internal rotor and outer rotor.
Improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention:
The quantity of permanent-magnet steel assembly is 1 ~ 4 pair; The quantity of permanent-magnet steel assembly is more, and flowmeter resolution is higher;
When outer rotor is the quantity of 4 teeth and permanent-magnet steel assembly when being 1 pair or 2 pairs, the permanent-magnet steel assembly is evenly arranged centered by the outer rotor revolving shaft; First sensor aperture and the second sensor aperture be symmetrical being arranged in the upper end cover centered by the outer rotor revolving shaft;
When outer rotor is 4 teeth, and when the quantity of permanent-magnet steel assembly is 3 pairs or 4 pairs, instantaneous delivery carries out the method for numerical integration and sets the position of permanent-magnet steel assembly and the position of first sensor aperture and the second sensor aperture, thereby by rationally arranging of magnet steel and magneto-dependent sensor, can be so that during constant flow, the square-wave signal of magneto-dependent sensor output is even.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention: the number of teeth of the gear ratio internal rotor of outer rotor is many 1, and oil storage tank I and oil storage tank II are symmetrically located at the both sides of eccentric throw line;
When the number of teeth of internal rotor≤4, the oil storage tank I is made of 4 sections circular arcs and 3 sections straight lines;
These 4 sections circular arcs are respectively:
Take the centre of gyration of outer rotor as the center of circle, the circular arc a take the root radius of outer rotor as radius;
Take the centre of gyration of internal rotor as the center of circle, the circular arc b take the root radius of internal rotor as radius;
Oil groove top small arc-shaped c, oil groove top small arc-shaped c answers the tooth top edge of as close as possible shown position outer rotor, but can not exceed the tooth top edge;
Oil groove bottom small arc-shaped d, the meshing point C of internal rotor and outer rotor and oil groove bottom small arc-shaped d coincide;
These 3 sections straight lines are respectively:
Connect successively straight line e and the straight line f of circular arc c and circular arc b, straight line e and straight line f then intersect at another meshing point A;
The straight line g that connects circular arc b and circular arc d.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention:
Have on the upper end cover two with bottom end cover on the oil storage tank I and the oil storage tank II mutually one by one over against the relief groove I of answering and relief groove II; Relief groove I and relief groove II are used for guaranteeing the axially loaded balance of internal rotor and outer rotor;
The degree of depth of relief groove I is 0.5 ~ 1mm.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention:
Internal rotor is provided with the internal rotor balancing orifice that vertically runs through internal rotor, and outer rotor is provided with the outer rotor balancing orifice that vertically runs through outer rotor, and the aperture of internal rotor balancing orifice and outer rotor balancing orifice is 0.5 ~ 1mm.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention: the bearing I is High precise ball bear or oilless bearing; The bearing II is oilless bearing; Outer rotor can rotate freely in the bearing II.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention: 4 sections circular arcs on the oil storage tank I and the acute angle of 3 sections straight line joints all carry out rounding to be processed, so that whole oil groove can be processed with CNC milling machine.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention: the first sensor aperture becomes 30 ° of angles to arrange centered by the outer rotor revolving shaft with the second sensor aperture.
Particularly, the present invention adopts following technical proposals: upper end cover, toroidal cavity housing and bottom end cover form high pressure resistant closed cavity, and a rooted tooth wheel shaft is arranged in the sealed cavity, are supported in respectively in the axis hole of upper end cover and bottom end cover.The gerotor type internal rotor is installed on the gear shaft, can be connected by High precise ball bear or oilless bearing between internal rotor and gear shaft.The internal rotor outside is and the outer rotor of its engagement, and the outer rotor outside is the oilless bearing that is fixed on the toroidal cavity housing, and outer rotor can rotate freely in oilless bearing.Outer rotor revolution axle center and internal rotor revolving shaft are felt in off-centre, and eccentric throw is e.On the outer rotor upper surface, centered by the outer rotor revolving shaft, can embed respectively many to magnet steel, magnet steel need to occur in pairs and N utmost point S interpolar every layout.In the upper end cover, become 30 ° and have two apertures centered by the outer rotor revolving shaft, high pressure resistant, a non-magnetic spacer is equipped with in the aperture lower end, respectively arranges one piece of magneto-dependent sensor on the spacer.
Permanent magnet on the described outer rotor can for 1 to (2 pieces) to 4 any amount to (8 pieces), but need to occur in pairs.The permanent magnet logarithm is more, and flowmeter resolution is higher.For outer rotor the situation of four teeth is arranged, when no more than 2 pairs of magnet steel number, only need magnet steel is evenly arranged centered by the outer rotor revolving shaft and get final product; When the magnet steel number then needs during more than 2 pairs to arrange the magnet steel position by calculating, make that magnet steel is inhomogeneous arranges, the position of magneto-dependent sensor is also wanted special and is determined.By rationally arranging of magnet steel and magneto-dependent sensor, can be so that during constant flow, the square-wave signal of magneto-dependent sensor output is even.That is, in the present invention, for outer rotor the situation of 4 teeth is arranged, when permanent magnet is arranged more than 2 pairs, then need the design parameter according to flowmeter, calculate the position of magnet steel, guarantee that when constant rate, the square wave frequency of output is constant.
Described bottom end cover has first, second oil groove that is communicated with respectively all annular seal spaces of side in the both sides of two revolving shaft lines.The first oil groove and the second oil groove be take the line of internal rotor revolving shaft and outer rotor revolving shaft as axis of symmetry, left-right symmetric.
The middle part of described bottom end cover two oil grooves has first, second hydraulic fluid port.
Have the shallow oil groove corresponding with the bottom end cover oil groove on the described upper end cover, to guarantee the axially loaded balance of inner and outer rotors.
Have the very little aperture of diameter that some are communicated with the upper and lower end face on the described inner and outer rotors, with balance upper and lower end face pressure.
When described outer rotor was permeability magnetic material, overlapping respectively outside two pairs of magnet steel had non-magnetic magnet steel cover again.
Described spacer center is welded with conducting magnetic column.
Described magneto-dependent sensor adopts the Hall switch integrated device.
The present invention compares with background technology, and the beneficial effect that has is:
1. compare with the Cylindrical Gear Meter of equal volume, rotating speed is lower when by same traffic, the pressure loss in the time of can reducing fluid by flowmeter; Reduce the pressure loss and can improve on the one hand system effectiveness, save the energy, help on the other hand to reduce the face leakage of flowmeter, improve flowmeter accuracy.
2. two-way cycloid rotor flowmeter high and low pressure side pressure reduction is little, and the suffered radial imbalance force of gear is little, and rotating speed is low, so bearing is not easy to wear, and long service life;
3. flowmeter internal rotor tooth curve is the equidistant curve of curtate epicycloid, and the outer rotor flank profil is and the partial arc flank profil of internal rotor conjugation that profile of tooth is simpler, than the elliptic gear handling ease;
Can arrange manyly to magnet steel on the outer rotor, more high pressure resistant oval gear flowmeter resolution is high;
4. only have a rooted tooth wheel shaft, upper and lower side covers only has an axis hole, can reduce axis hole to the strength reduction of end cap up and down, reduces up and down end cap deformation quantity under high pressure.
5, the advantage of maximum of the present invention is when the flowmeter volume is identical, and by identical flow, inner and outer rotors rotating speed of the present invention is lower, and rotating speed is low can to reduce the pressure loss.
VS2 type gear meter in the VS Series Gear flowmeter that Germany Wei Shi company produces is when being 100L/min by flow, rotating speed is about 3600r/min, and the of the present invention two-way cycloid rotor flowmeter identical with VS2 type gear meter overall volume be when being 100L/min by flow, and rotating speed only has 500r/min.
Description of drawings
Fig. 1 is the sectional structure synoptic diagram of high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention;
Fig. 2 is the structure exploded perspective view of Fig. 1, among this figure, 2 pairs of magnet steel (i.e. 4 pieces of permanent-magnet steels 9) is set on the outer rotor 4;
Fig. 3 is the arrangement figure when on the outer rotor 4 among Fig. 13 pairs of magnet steel (i.e. 6 pieces of permanent-magnet steels 9) being set;
Among Fig. 3: the schematic top plan view of outer rotor 4 during (a) for 3 pairs of magnet steel of layout; The vertical view of upper end cover 1 during (b) for 3 pairs of magnet steel of layout;
Fig. 4 is the arrangement figure when on the outer rotor 4 among Fig. 14 pairs of magnet steel (i.e. 8 pieces of permanent-magnet steels 9) being set;
Among Fig. 4: the schematic top plan view of outer rotor 4 during (a) for 4 pairs of magnet steel of layout; The vertical view of upper end cover 1 during (b) for 4 pairs of magnet steel of layout;
Fig. 5 is the schematic top plan view of the bottom end cover 3 among Fig. 1;
Fig. 6 is the elevational schematic view of the upper end cover 1 among Fig. 1;
Fig. 7 is a kind of embodiment figure of two logical oil grooves (21,22) when internal rotor has 3 teeth, outer rotors that 4 teeth are arranged on the bottom end cover (3) among Fig. 1;
Fig. 8 is a kind of embodiment figure of two logical oil grooves (21,22) when internal rotor has 4 teeth, outer rotors that 5 teeth are arranged on the middle bottom end cover (3) among Fig. 1;
Figure (a) and to scheme (b) be respectively the situation of inner and outer rotors when being positioned at the different position of engagement among Fig. 8.
Fig. 9 is the principle of work synoptic diagram of Fig. 1;
Figure 10 is the enlarged diagram of X section among Fig. 1.
Figure 11 is the schematic top plan view of internal rotor 5 among Fig. 1.
Figure 12 is the schematic top plan view of outer rotor 4 among Fig. 1.
Among the figure: 1. upper end cover, 2. housing, 3. bottom end cover, 4. outer rotor, 5. internal rotor, 6. gear shaft, 7. bearing, 8. bearing, 9-12. magnet steel, 13. magnet steel covers, 14. magnet steel covers, 15. antifreeze plates, 16. magneto-dependent sensor, 17. sensor apertures, 18. sensor apertures, 19. hydraulic fluid ports, 20. hydraulic fluid port, 21. logical oil grooves, 22. logical oil grooves, 23. balancing slits, 24. balancing slit, 25. O-ring seals, 26. internal rotor balancing orifices 26, outer rotor balancing orifice 27.
Embodiment
The invention will be further described below in conjunction with drawings and Examples.
Be connected by bearing I 8 between internal rotor 5 and the gear shaft 6, bearing I 8 can be selected High precise ball bear or oilless bearing, and therefore, internal rotor 5 can rotate with respect to gear shaft 6.
The outside of internal rotor 5 is and the outer rotor 4 of its engagement that the outside of outer rotor 4 is that the bearing II 7(bearing II 7 that is fixed on the toroidal cavity housing 2 can be selected oilless bearing), outer rotor 4 can rotate freely in bearing II 7.The revolution axle center of outer rotor 4 and the revolving shaft of internal rotor 5 are felt in off-centre, and eccentric throw is e.Internal rotor 5 outer walls that rotate in the inner chamber of outer rotor 4 and outer rotor 4 inwalls form the annular seal space that 4 volume cycles change.
In the upper surface of outer rotor 4 (i.e. the face of close upper end cover 1) 2 pairs permanent-magnet steel assembly is set centered by outer rotor 4 revolving shaftes, every pair of permanent-magnet steel assembly becomes the permanent-magnet steel 9 of 180 ° of layouts to form centered by outer rotor 4 revolving shaftes by two; Therefore, that is, in the upper surface of outer rotor 44 permanent-magnet steels 9 are set uniformly, the angle of the center line of these 4 permanent-magnet steels 9 is 90o.The N utmost point and the S of adjacent permanent-magnet steel 9 extremely mutually stagger (that is, the N utmost point S of adjacent permanent-magnet steel 9 is extremely opposite).
Centered by outer rotor 4 revolving shaftes, becoming 30 ° to be provided with first sensor aperture 17 and the second sensor aperture 18(namely on the upper end cover 1, angle between first sensor aperture 17 and the second sensor aperture 18 center lines is 30 °), first sensor aperture 17 and the second sensor aperture 18 all run through upper end cover 1, in first sensor aperture 17 and the second sensor aperture 18, be provided with separately high pressure resistant, a non-magnetic spacer 15, arrange one piece of magneto-dependent sensor 16 on the every spacer 15.
When outer rotor 4 was permeability magnetic material, cover had non-magnetic magnet steel cover 13 in the outside of permanent-magnet steel 9, and magnet steel cover 13 and spacer 15 adopt non-magnetic stainless steel material to make.Magneto-dependent sensor 16 adopts Hall switch integrated devices (the locking-typed Hall switch integrated device of the single output of ZH3070 series that for example can select in the Hangzhou Electronics Co., Ltd. suddenly to produce).Upper end cover 1, toroidal cavity housing 2, bottom end cover 3, outer rotor 4 and internal rotor 5 adopt the plow-steel material to make; Toroidal cavity housing 2 and bottom end cover 3 or toroidal cavity housing 2 and upper end cover 1 can be made of one.
As shown in figure 10, at spacer 15(as antifreeze plate) the center be welded with conducting magnetic column 21, this structure can obviously strengthen the magnetic induction density of magneto-dependent sensor 16 present positions.
Be provided with oil storage tank I 21 and oil storage tank II 22 at bottom end cover 3, connect internal rotor 5 revolving shaftes at the subpoint of bottom end cover 3 and outer rotor 4 revolving shaftes at the subpoint of bottom end cover 3 as the eccentric throw line; Oil storage tank I 21 and oil storage tank II 22 be symmetrical both sides that are positioned at the eccentric throw line respectively.In rotation process, each oil storage tank is connected with two annular seal spaces respectively.As shown in Figure 5, oil storage tank I 21 with all link to each other with all annular seal spaces that self are in eccentric throw line homonymy, same, oil storage tank II 22 with all link to each other with all annular seal spaces that self are in eccentric throw line homonymy.
For the number of teeth of internal rotor 5 more than for the cycloid flowmeter of 4 teeth, the shape of oil groove can be with reference to the shape of gerotor pump crescent, the inner edge of gerotor pump crescent shape oil groove is as the center of circle take the internal rotor centre of gyration, circular arc take the root radius of internal rotor as radius, the outer rim of crescent shape oil groove then be the centre of gyration take outer rotor as the center of circle, the circular arc take the root radius of outer rotor as radius.But for cycloid rotor type flowmeter of the present invention, in order to pursue lower rotating speed, usually use the less number of teeth (being 3 teeth in this embodiment).Because its rotor number of teeth few (internal rotor is no more than 4 teeth usually), and eccentric throw is large, and traditional crescent shape is applicable (can cause and can't seal) no longer.Therefore in order to make internal rotor 5 and outer rotor 4 in rotation process, remain that oil suction chamber and the sealing that goes out oil pocket are (namely, the sealing of the annular seal space that oil storage tank I 21 and he are communicated with and oil storage tank II 22 and the annular seal space that he is communicated with), also long-pending in order to increase as much as possible logical pasta, reduce the pressure loss, adopt oil storage tank I 21 shown in Figure 7 and oil storage tank II 22.
Fig. 7 is the shape of internal rotor 5 two oil grooves (oil storage tank I 21 and oil storage tank II 22) that bottom end cover 3 is opened when being 3 teeth, and oil storage tank I 21 and oil storage tank II 22 are symmetrical along the eccentric throw line.The below sets forth as an example of oil storage tank I 21 example:
Oil storage tank I 21 mainly is made of 4 sections circular arcs and 3 sections straight lines.
These 4 sections circular arcs are respectively:
Take the centre of gyration of outer rotor 4 as the center of circle, and the circular arc a take the root radius of outer rotor 4 as radius,
Take the circular arc b of internal rotor 5 centres of gyration as the center of circle, take the root radius of internal rotor 5 as radius,
Oil groove top small arc-shaped c,
Oil groove bottom small arc-shaped d;
Three sections straight lines are respectively:
The straight line e, the f that connect circular arc b and circular arc c,
The straight line g that connects circular arc b and circular arc d.
Above-mentioned circular arc and straight line are characterised in that: the acute angle of all circular arcs, straight line joint is carried out the rounding processing, so that whole oil groove can be processed with CNC milling machine.
Specifically do the description below explanation:
For internal rotor 53 teeth are arranged, outer rotor 4 has the situation of 4 teeth, (what internal rotor 5 contacted with outer rotor 4 in the reality is a line to have 4 meshing points, then be the point that internal rotor 5 curves contact with outer rotor 4 curves at projection view, totally 4), the projected position of these four meshing points on upper end cover 1 is along with the rotation of internal rotor 5 and outer rotor 4 changes.Four points of ABCD shown in Fig. 7 are meshing point projections on upper end cover 1 when outer rotor 4 and internal rotor 5 are on the ad-hoc location.Specifying of ad-hoc location: for internal rotor 53 teeth are arranged, outer rotor 4 has the situation of 4 teeth, and four points of ABCD refer to when outer rotor 4 is in as shown in Figure 7 position about eccentric throw line symmetry, the projected position of four meshing points on upper end cover 1; For internal rotor 54 teeth are arranged, outer rotor 4 has the situation of 5 teeth, four points of described ABCD do not occur at synchronization, wherein 2 of AB are when being in shown in Fig. 8 (a) position about eccentric throw line symmetry when outer rotor 4, be positioned at the subpoint of two meshing points of upper end cover 1 projection the first half, 2 of CD work as outer rotor 4 on the basis of Fig. 8 (a), (or clockwise) rotation half tooth (is 4 teeth to internal rotor 5 counterclockwise, outer rotor 4 is the situation of 5 teeth, (or clockwise) rotation is 36 ° namely counterclockwise) after, be positioned at the subpoint of two meshing points of upper end cover 1 projection the latter half, shown in Fig. 8 (b).
Such as the movement locus that heavy line among Fig. 7 is any meshing point when internal rotor 5, outer rotor 4 rotation, this track can draw by the motion of computer simulation inner and outer rotors.
Straight line e satisfied A point shown in Figure 7, and was tangential on the A point with the movement locus line of meshing point.
The length of the radius of small arc-shaped c and straight line e is not critical size, but as shown in Figure 7, should satisfy the upper any point of small arc-shaped c in Fig. 7 during outer rotor 4 position the distance of the drop shadow curve of outer rotor 4 inside surfaces on upper end cover 1 greater than 3mm, and straight line e and small arc-shaped c be except the A point, can not with among Fig. 7 during outer rotor 4 position the drop shadow curve of outer rotor 4 inside surfaces on upper end cover 1 intersect.
Straight line g and small arc-shaped d are as shown in Figure 7, should satisfy small arc-shaped d and cross C point shown in Figure 7, and straight line g, small arc-shaped d and the arc transition line that connects them be all in the outside of the inner small arc-shaped curve of path of action line (heavy line among Fig. 7), and straight line g, small arc-shaped d and connect any point on their the arc transition line apart from the distance of any point on the inner small arc-shaped curve of path of action line (heavy line among Fig. 7) greater than 1mm.
Meshing point A shown in the straight line f connection layout 7 and circular curve c(joining place rounding), it should satisfy whole section straight line and all is positioned at when the inside of internal rotor 5 internal rotor 5 outside surfaces drop shadow curve on upper end cover 1 during in position shown in Figure 7, and straight line f upper except distance meshing point A 3mm with other any points the interior point to the distance of internal rotor 5 outside surfaces any point in the drop shadow curve on the upper end cover 1 when internal rotor 5 is positioned at position shown in Figure 7 greater than 3mm.
In this example, the radius of small arc-shaped c is 5mm, and the radius of small arc-shaped d is 2mm.
Be respectively equipped with logical hydraulic fluid port I 19 and logical hydraulic fluid port II 20 at bottom end cover 3, logical hydraulic fluid port I 19 is connected with oil storage tank I 21, and logical hydraulic fluid port II 20 is connected with oil storage tank II 22; Logical hydraulic fluid port I 19 be positioned at oil storage tank I 21 under, logical hydraulic fluid port II 20 be positioned at oil storage tank II 22 under.
The remarks explanation: logical hydraulic fluid port I 19, logical hydraulic fluid port II 20 are as oil-in and oil-out; When oil-in and oil-out transposing, internal rotor 5 changes sense of rotation simultaneously with outer rotor 4.
Be provided with oil storage tank I 21 and oil storage tank II 22 mutually one by one over against the equal pressure oil groove I 23 of answering and equal pressure oil groove II 24 at upper end cover 1, namely, all the shape of cross section of pressure oil groove I 23 is fully with oil storage tank I 21, and all the shape of cross section of pressure oil groove II 24 is fully with oil storage tank II 22.All the degree of depth of pressure oil groove I 23 and equal pressure oil groove II 24 all only is 0.5mm.Thereby guarantee the axially loaded balance of internal rotor 5 and outer rotor 4, that is, make the oil liquid pressure distribution of the upper and lower end face of inner and outer rotors identical, reach the effect of balancing axial thrust, prevent that the inner and outer rotors axially loaded is uneven.
Although, upper end cover 1 is provided with oil storage tank I 21 and oil storage tank II 22 mutually one by one over against the equal pressure oil groove I 23 of answering and equal pressure oil groove II 24, but when internal rotor 5 and outer rotor 4 produces when being offset play up and down, because the effect of hydraulic card clamping force still may make internal rotor 5 and outer rotor 4 be pressed on the end face of upper end cover 1 or bottom end cover 3.The present invention is at the internal rotor balancing orifice 26 of internal rotor 5 settings and the outer rotor balancing orifice 27 that arranges at outer rotor 4, can short circuit internal rotor 5 and outer rotor 4 upper and lower end faces between unbalanced pressure, prevent hydraulic card clamping force, help to reduce the end-face friction of internal rotor 5 and outer rotor 4.
The principle of work of high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention as shown in Figure 9, the course of work is specific as follows:
Its core parts are the cycloidal gear of a pair of off-centre (eccentric throw is e) engagement, the number of teeth of its outer rotor 4
The number of teeth than internal rotor 5
Many 1, in the engagement rotation process, can form
Individual independently sealed volume is (when having the even number cavity volume, always
Individual sealed volume and an oil storage tank are communicated with, in addition
Individual sealed volume and another oil storage tank are communicated with; And when the odd number cavity volume was arranged, along with the rotation of inner and outer rotors, the sealed volume that links to each other with one of them oil storage tank was
Individual (or
Individual), and and the sealed volume that is connected of another oil storage tank be
Individual (or
Individual)), along with the rotation of internal rotor 5 and outer rotor 4, the volume of each sealed volume constantly changes.When flowmeter right side dotted line oil groove is oil feed groove (situation was opposite therewith when the left-hand broken line oil groove was oil feed groove), oil liquid pressure is greater than the pressure of two sealed volumes in left side in two sealed volumes in right side.It is large that two sealed volumes in right side constantly become under pressure, all is rotated counterclockwise thereby promote inner and outer rotors.
The remarks explanation: in rotary course, the cavity volume number is constant, and just certain cavity volume can become very little sometimes.
The process that (a) enters flowmeter A chamber to (d) for fluid among Fig. 9, and (d) to (f) process for fluid outflow flowmeter A chamber.Shown in (a) among Fig. 9, this moment, A chamber volume was minimum; Internal rotor 5 and outer rotor 4 are rotated counterclockwise under the effect of right atrial pressure oil simultaneously, and internal rotor 5 rotating speeds are very fast, and outer rotor 4 rotating speeds are slower.When forwarding position shown in (b) to, A chamber volume enlarges, and when forwarding (c) position to, A chamber volume further enlarges.Along with the continuous expansion of A chamber volume, fluid constantly enters flowmeter, among the A chamber.When arriving (d) position, A chamber volume is maximum, and the process that fluid enters flowmeter finishes.Internal rotor 5 and outer rotor 4 continue motion afterwards, arrive (e) position, and this moment, A chamber volume began to reduce, and the fluid in the A chamber is forced out from going out the oil groove of left side, and when forwarding (f) position to, it is minimum that A chamber volume reaches, and the oil extraction process finishes.
This flowmeter in the course of the work, a tooth of outer rotor 4 turns over a week, namely finishes a working cycle of finishing, and realizes that fluid enters flowmeter and extrudes the flowmeter process once.Outer rotor 4 for n tooth arranged whenever turns around, and will n the working cycle identical with the A chamber occur.For example have the outer rotor of 4 teeth to rotate a circle in the diagram, flowmeter can pass through 4 times of volumes when the maximum of A chamber
Liquid.So, fluid just can continuously enter flowmeter from oil feed groove, and is split into one by one liquid piece, constantly is forced out flowmeter again.
During actual the use, when if logical hydraulic fluid port I 19 is led to hydraulic fluid port II 20 for oil-out for oil-in, logical hydraulic fluid port I 19 links to each other with flowline (oil inlet pipe) with the oil inlet pipe (flowline) in the external world respectively with logical hydraulic fluid port II 20, the flow process of fluid in flowmeter of the present invention is followed successively by: fluid enters into oil storage tank I 21 by logical hydraulic fluid port I 19, and then enter into upper end cover 1 and bottom end cover 3 and toroidal cavity housing 2 formed closed containing cavities, further promote internal rotor 5 and outer rotor 4 rotations, fluid is divided, and finally enter in the oil storage tank II 22, flow out flowmeter by logical hydraulic fluid port II 20, enter flowline.If when logical hydraulic fluid port II 20 was led to hydraulic fluid port I 19 for oil-out for oil-in, the fluid flow process was opposite with said process.
When internal rotor 5 and outer rotor 4 rotation, the permanent-magnet steel 9 that outer rotor 4 is embedded in is the sensitizing range of inswept magneto-dependent sensor 16 correspondingly, makes magneto-dependent sensor 16 sense the variation of permanent magnetic field, changes output signal level.This signal is transported in the secondary instrument, thereby obtains the concrete flow (this is with existing routine techniques) of fluid.By the theory of engagement of cycloid internal gear as can be known, when flow kept invariable, the angular velocity of interior outer rotor changed.But for the outer rotor that 4 teeth are arranged, rotate the fluctuation of speed four times within the week, so when only having a pair of or during two pairs of permanent-magnet steels 9, can be with permanent-magnet steel 9 circumferentially evenly distributing along outer rotor 4, then only having could be to a magneto-dependent sensor 16 effect wherein when outer rotor 4 Rotate 180s ° or 90 °, then when constant flow, the square-wave signal of magneto-dependent sensor 16 outputs also is constant, and the frequency of square wave be directly proportional with fluid flow by flowmeter (the square wave number of namely measuring magneto-dependent sensor 16 outputs by secondary instrument can obtain the flow information by flowmeter), the aperture that magneto-dependent sensor 16 is housed on the upper end cover 1 (namely at this moment, first sensor aperture 17 and the second sensor aperture 18) position do not need particular design yet, can be at an arbitrary position, if guarantee permanent magnet can be inswept should the zone.
Fig. 8 is the shape (its shape and feature are equal to oil storage tank I 21 and the oil storage tank II 22 among the embodiment 1) of internal rotor 5 two oil grooves that bottom end cover 3 is opened when being 4 teeth.
The method for arranging of permanent-magnet steel 9 is different from embodiment 1, specifically arranges according to following computing method:
All permanent-magnet steels 9 are positioned at the upper surface of outer rotor 4, on the same circle take outer rotor 4 revolving shaftes as the center of circle (this radius of a circle can arbitrarily be got according to actual needs).At first suppose outer rotor 4 be positioned at shown in Fig. 8 (a) about the axisymmetric position of off-centre, and this position is made as zero-bit.At will get a position in the outside of the upper surface of outer rotor 4 dedendum circle afterwards, as the placement location of first piece of permanent-magnet steel 9.Afterwards according to the instantaneous delivery formula of cycloid internally meshed rotor (for example can with reference to the formula (5.4) in " theoretical research of interior engagement cycloid gear pump and calculating "), can obtain the instantaneous delivery of outer rotor 4 at an arbitrary position the time, turn over when arbitrarily angled fluid volume by flowmeter by then can know outer rotor 4 to the instantaneous delivery integration.Supposing needs to arrange that n to magnet steel, only need make flowmeter outer rotor 4 turn over certain angle
, so that turning over this angle
The time, by the flowmeter fluid volume when fluid volume by flowmeter just in time turns a whole circle for outer rotor 4
Then second piece of magnet steel becomes centered by outer rotor 4 revolving shaftes with first piece of magnet steel
The degree angle gets final product.Computing method for the magnet steel position such as the 3rd piece, the 4th piece are identical identical with second piece, get final product by that analogy.
Claims (8)
1. high voltage-resistant bi-directional cycloid rotor flowmeter, it is characterized in that: comprise by upper end cover (1), toroidal cavity housing (2) and bottom end cover (3) forming high pressure resistant closed cavity, be respectively equipped with gear shaft (6), intermeshing internal rotor (5) and outer rotor (4) in the described toroidal cavity housing (2), the up and down two ends of described gear shaft (6) rely on transition fit to realize linking to each other with upper end cover (1) and bottom end cover (3) respectively; Gear shaft (6) is sleeved in the inner chamber of internal rotor (5), internal rotor (5) is sleeved in the inner chamber of outer rotor (4), described internal rotor (5) is rotatedly connected by bearing I (8) and gear shaft (6), and described outer rotor (4) is rotatedly connected by bearing II (7) and toroidal cavity housing (2);
The revolving shaft of the revolution axle center of described outer rotor (4) and internal rotor (5) is felt in off-centre, and the internal rotor that rotates in the inner chamber of outer rotor (4) (5) outer wall and outer rotor (4) inwall form the annular seal space of several volume cycle variation;
Centered by outer rotor (4) revolving shaft 1 ~ 4 pair permanent-magnet steel assembly is being set on the upper surface of outer rotor (4), described every pair of permanent-magnet steel assembly becomes the permanent-magnet steel (9) of 180 ° of layouts to form centered by outer rotor (4) revolving shaft by two; The described N utmost point and the S that is positioned at the adjacent permanent-magnet steel (9) on the outer rotor (4) staggers extremely mutually;
First sensor aperture (17) and the second sensor aperture (18) are set in upper end cover (1), described first sensor aperture (17) and the second sensor aperture (18) all run through upper end cover (1), be provided with separately high pressure resistant, a non-magnetic spacer (15) in first sensor aperture (17) and the second sensor aperture (18), the upper one piece of magneto-dependent sensor (16) of arranging of described every spacer (15);
Be provided with oil storage tank I (21) and oil storage tank II (22) at bottom end cover (3), connect internal rotor (5) revolving shaft at the subpoint of bottom end cover (3) and outer rotor (4) revolving shaft at the subpoint of bottom end cover (3) as the eccentric throw line; Described oil storage tank I (21) and oil storage tank II (22) lay respectively at the both sides of eccentric throw line; Described internal rotor (5) outer wall and outer rotor (4) inwall form annular seal space that several volume cycle changes and are connected with in oil storage tank I (21) and the oil storage tank II (22) any one;
Be respectively equipped with logical hydraulic fluid port I (19) and logical hydraulic fluid port II (20) at bottom end cover (3), described logical hydraulic fluid port I (19) is connected with oil storage tank I (21), and logical hydraulic fluid port II (20) is connected with oil storage tank II (22);
Be provided with and oil storage tank I (21) and oil storage tank II (22) mutually one to one all pressure oil groove I (23) and equal pressure oil groove II (23) at upper end cover (1), thereby guarantee the axially loaded balance of internal rotor (5) and outer rotor (4).
2. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 1 is characterized in that:
The quantity of described permanent-magnet steel assembly is 1 ~ 4 pair;
When outer rotor (4) is the quantity of 4 teeth and permanent-magnet steel assembly when being 1 pair or 2 pairs, the permanent-magnet steel assembly is evenly arranged centered by outer rotor (4) revolving shaft; Described first sensor aperture (17) and the second sensor aperture (18) be symmetrical being arranged in the upper end cover (1) centered by outer rotor (4) revolving shaft;
When outer rotor (4) is 4 teeth, and when the quantity of permanent-magnet steel assembly is 3 pairs or 4 pairs, instantaneous delivery carries out the method for numerical integration and sets the position of permanent-magnet steel assembly and the position of first sensor aperture (17) and the second sensor aperture (18), thereby by rationally arranging of magnet steel and magneto-dependent sensor, can be so that during constant flow, the square-wave signal of magneto-dependent sensor output is even.
3. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 2 is characterized in that:
The number of teeth of the gear ratio internal rotor (5) of described outer rotor (4) is many 1, and described oil storage tank I (21) and oil storage tank II (22) are symmetrically located at the both sides of eccentric throw line;
When the number of teeth of internal rotor (5)≤4, described oil storage tank I (21) is made of 4 sections circular arcs and 3 sections straight lines;
These 4 sections circular arcs are respectively:
Take the centre of gyration of outer rotor (4) as the center of circle, the circular arc a take the root radius of outer rotor (4) as radius;
Take the centre of gyration of internal rotor (5) as the center of circle, the circular arc b take the root radius of internal rotor (5) as radius;
Oil groove top small arc-shaped c, described oil groove top small arc-shaped c answers the tooth top edge of as close as possible shown position outer rotor (4), but can not exceed the tooth top edge;
Oil groove bottom small arc-shaped d, the meshing point C of internal rotor (5) and outer rotor (4) and oil groove bottom small arc-shaped d coincide;
These 3 sections straight lines are respectively:
Connect successively straight line e and the straight line f of circular arc c and circular arc b, straight line e and straight line f then intersect at another meshing point A;
The straight line g that connects circular arc b and circular arc d.
4. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 3 is characterized in that: have on the upper end cover (1) two with bottom end cover (3) on oil storage tank I (21) and oil storage tank II (22) mutually one by one over against the relief groove I (23) of answering and relief groove II (24); Described relief groove I (23) and relief groove II (24) are used for guaranteeing the axially loaded balance of internal rotor (5) and outer rotor (4);
The degree of depth of described relief groove I (23) is 0.5 ~ 1mm.
5. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 4 is characterized in that:
Described internal rotor (5) is provided with the internal rotor balancing orifice (26) that vertically runs through internal rotor (5), outer rotor (4) is provided with the outer rotor balancing orifice (27) that vertically runs through outer rotor (4), and the aperture of described internal rotor balancing orifice (26) and outer rotor balancing orifice (27) is 0.5 ~ 1mm.
6. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 5 is characterized in that:
Described bearing I (8) is High precise ball bear or oilless bearing;
Bearing II (7) is oilless bearing; Outer rotor (4) can rotate freely in bearing II (7).
7. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 6 is characterized in that:
4 sections circular arcs on the oil storage tank I (21) and the acute angle of 3 sections straight line joints all carry out rounding to be processed, so that whole oil groove can be processed with CNC milling machine.
8. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 7 is characterized in that:
First sensor aperture (17) becomes 30 ° of angles to arrange centered by outer rotor (4) revolving shaft with the second sensor aperture (18).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201210452717.0A CN102914338B (en) | 2012-11-13 | 2012-11-13 | High-pressure resistant two-way cycloid rotameter |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210452717.0A CN102914338B (en) | 2012-11-13 | 2012-11-13 | High-pressure resistant two-way cycloid rotameter |
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| CN102914338A true CN102914338A (en) | 2013-02-06 |
| CN102914338B CN102914338B (en) | 2014-08-13 |
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| CN201210452717.0A Expired - Fee Related CN102914338B (en) | 2012-11-13 | 2012-11-13 | High-pressure resistant two-way cycloid rotameter |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104154960A (en) * | 2014-08-01 | 2014-11-19 | 衢州市鼎盛化工科技有限公司 | Hall-effect large-diameter pipeline flowmeter |
| CN104949716A (en) * | 2015-06-18 | 2015-09-30 | 合肥精特仪表有限公司 | Corrosion-resistant small-pulse equivalent flow meter |
| CN108061234A (en) * | 2018-01-12 | 2018-05-22 | 中国航发哈尔滨东安发动机有限公司 | A kind of oil pump interstage casings molded line structure |
| CN108344462A (en) * | 2017-01-23 | 2018-07-31 | 佛山市众泽机电科技有限公司 | A kind of three-apexed rotor flowmeter |
| CN108955781A (en) * | 2018-06-25 | 2018-12-07 | 浙江工业大学 | A kind of digital frequency conversion measurement controller of strong corrosive liquid medium flow |
| DE102019001466A1 (en) * | 2019-03-04 | 2020-09-10 | Alexander Leonhardt | Dosing measuring sensor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104154960A (en) * | 2014-08-01 | 2014-11-19 | 衢州市鼎盛化工科技有限公司 | Hall-effect large-diameter pipeline flowmeter |
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| CN108061234A (en) * | 2018-01-12 | 2018-05-22 | 中国航发哈尔滨东安发动机有限公司 | A kind of oil pump interstage casings molded line structure |
| CN108955781A (en) * | 2018-06-25 | 2018-12-07 | 浙江工业大学 | A kind of digital frequency conversion measurement controller of strong corrosive liquid medium flow |
| CN108955781B (en) * | 2018-06-25 | 2020-03-17 | 浙江工业大学 | Digital frequency conversion metering controller for flow of strong corrosive liquid medium |
| DE102019001466A1 (en) * | 2019-03-04 | 2020-09-10 | Alexander Leonhardt | Dosing measuring sensor |
| DE102019001466B4 (en) * | 2019-03-04 | 2020-10-15 | Alexander Leonhardt | Dosing measuring sensor |
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