CN102914338B - High-pressure resistant two-way cycloid rotameter - Google Patents
High-pressure resistant two-way cycloid rotameter Download PDFInfo
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- CN102914338B CN102914338B CN201210452717.0A CN201210452717A CN102914338B CN 102914338 B CN102914338 B CN 102914338B CN 201210452717 A CN201210452717 A CN 201210452717A CN 102914338 B CN102914338 B CN 102914338B
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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, in all multi-parameter detector tables in the fields such as process industry, public utilities and accumulating handing-over, occupies larger proportion.Volumeter, because precision is high, be not subject to pipeline mounting condition to limit, can be used for the advantages such as high viscosity liquid is measured, measurement range is wide, is widely used at industrial control field.Traditional volumeter using gear as transmission body, mostly is noncircular gear flowmeter, as oval gear flowmeter, Roots-type flow meter etc.Wherein Roots-type flow meter, because cannot be from engagement, needs the auxiliary engagement of additional 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, and the N utmost point two magnet steel extremely contrary with S that become 180 ° of layouts centered by gear shaft are installed on an elliptic gear end face therein; And in upper end cover, have layout Hall element in 90 ° centered by same gear shaft, utilize the two-way flow that the phase differential of two sensors output pulses can test fluid.But elliptic gear complex structure, processing difficulties, the high and precision of processing cost is difficult to ensure, and in invention CN1828233A, disclosed high voltage-resistant bi-directional elliptic gear flow meter can only be arranged a pair of magnet steel, resolution is lower.
Existing high voltage bearing Cylindrical Gear Meter in the market, the VS Series Gear flowmeter of producing as German Wei Shi company, adopt a pair of intermeshing cylindrical gear to do transmission body, and in upper end cover, arrange that permanent magnet and Hall element are 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 causing is thus larger, and because flowmeter high and low pressure side pressure reduction is larger, gear is subject to radial imbalance force larger, the easy wear out failure when the high rotating speed and under the effect of uneven radial force for the High precise ball bear that connects gear rotor and gear shaft.
Summary of the invention
The present invention will approaching technical matters be to provide a kind of high voltage-resistant bi-directional cycloid rotor flowmeter that is easy to processing and 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, in toroidal cavity housing, be respectively equipped with gear shaft, intermeshing internal rotor and outer rotor, the two ends up and down of gear shaft rely on transition fit realization to be connected 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 bias, and the internal rotor outer wall rotating in the inner chamber of outer rotor and outer rotor inwall form the annular seal space of several volume cycle variation;
The permanent-magnet steel assembly of 1 ~ 4 pair is set on the upper surface of outer rotor centered by outer rotor revolving shaft, and every pair of permanent-magnet steel assembly becomes the permanent-magnet steel of 180 ° of layouts to form centered by outer rotor revolving shaft by two; The N utmost point and the S that are positioned at the adjacent permanent-magnet steel on 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, in first sensor aperture and the second sensor aperture, be provided with separately high pressure resistant, a non-magnetic spacer, on every spacer, arrange one piece of magneto-dependent sensor;
On bottom end cover, be provided with oil storage tank I and oil storage tank II, connect internal rotor revolving shaft at the subpoint of bottom end cover and outer rotor revolving shaft at the subpoint of bottom end cover as 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 any one in oil storage tank I and oil storage tank II;
On bottom end cover, be respectively equipped with logical hydraulic fluid port I and logical hydraulic fluid port II, logical hydraulic fluid port I is connected with oil storage tank I, and logical hydraulic fluid port II is connected with oil storage tank II;
On upper end cover, be provided with and oil storage tank I and oil storage tank II all pressure oil groove I and all pressure oil groove II one to one mutually, 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;
In the time that the outer rotor quantity that is 4 teeth and permanent-magnet steel assembly is 1 pair or 2 pairs, permanent-magnet steel assembly is evenly arranged centered by outer rotor revolving shaft; First sensor aperture and the second sensor aperture be symmetrical being arranged in upper end cover centered by outer rotor revolving shaft;
In the time that 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 make constant flow time, 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;
In the time of the number of teeth≤4 of internal rotor, oil storage tank I is made up of 4 sections of circular arcs and 3 sections of straight lines;
These 4 sections of circular arcs are respectively:
Taking the centre of gyration of outer rotor as the center of circle, the circular arc a taking the root radius of outer rotor as radius;
Taking the centre of gyration of internal rotor as the center of circle, the circular arc b taking the root radius of internal rotor as radius;
Oil groove top small arc-shaped c, oil groove top small arc-shaped c should, as far as possible near the tooth top edge of shown position outer rotor, still can not exceed 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 of straight lines are respectively:
The straight line e and the straight line f that connect successively circular arc c and circular arc b, straight line e and straight line f intersect at another meshing point A;
Connect the straight line g of circular arc b and circular arc d.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention:
On upper end cover, have two with oil storage tank I on bottom end cover and oil storage tank II positive corresponding relief groove I and relief groove II one by one mutually; Relief groove I and relief groove II are 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 longitudinally runs through internal rotor, and outer rotor is provided with the outer rotor balancing orifice that longitudinally 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: bearing I is High precise ball bear or oilless bearing; Bearing II is oilless bearing; Outer rotor can rotate freely in bearing II.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention: 4 sections of circular arcs in oil storage tank I and the acute angle of 3 sections of straight line joints all carry out rounding processing, and whole oil groove can be processed by CNC milling machine.
Further improvement as high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention: first sensor aperture becomes 30 ° of angles to arrange with the second sensor aperture centered by outer rotor revolving shaft.
Particularly, the present invention adopts following technical proposals: upper end cover, toroidal cavity housing and bottom end cover form high pressure resistant closed cavity, has a rooted tooth wheel shaft in sealed cavity, is supported in respectively in the axis hole of upper end cover and bottom end cover.Gerotor type internal rotor is installed on gear shaft, between internal rotor and gear shaft, can be connected by High precise ball bear or oilless bearing.Internal rotor outside is the outer rotor engaging with it, and outer rotor outside is the oilless bearing being fixed on 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 bias, and eccentric throw is e.On outer rotor upper surface, centered by outer rotor revolving shaft, can embed respectively multipair magnet steel, magnet steel needs appearance in pairs and N utmost point S interpolar every layout.In upper end cover, become 30 ° to have two apertures centered by outer rotor revolving shaft, high pressure resistant, a non-magnetic spacer is equipped with in aperture lower end, one piece of magneto-dependent sensor of each layout on spacer.
Permanent magnet on described outer rotor can be 1 to (2 pieces) to 4 any amount to (8 pieces), but need to occur in pairs.Permanent magnet logarithm is more, and flowmeter resolution is higher.There is the situation of four teeth for outer rotor, in the time of no more than 2 pairs of magnet steel number, only magnet steel need be evenly arranged centered by outer rotor revolving shaft; When magnet steel number needs to arrange magnet steel position by calculating during more than 2 pairs, 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 make constant flow time, the square-wave signal of magneto-dependent sensor output is even.That is, in the present invention, there is the situation of 4 teeth for outer rotor, in the time having more than 2 pairs permanent magnet, need the design parameter according to flowmeter, calculate the position of magnet steel, ensure that, in the time of 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 a side in the both sides of two revolving shaft lines.The first oil groove and the second oil groove are taking the line of internal rotor revolving shaft and outer rotor revolving shaft as axis of symmetry, symmetrical.
The middle part of described bottom end cover two oil grooves has first, second hydraulic fluid port.
On described upper end cover, have the shallow oil groove corresponding with bottom end cover oil groove, to ensure the axially loaded balance of inner and outer rotors.
On described inner and outer rotors, have the very little aperture of diameter that some are communicated with upper and lower end face, with balance upper and lower end face pressure.
When described outer rotor is permeability magnetic material, outside two pairs of magnet steel, cover has non-magnetic magnet steel cover more respectively.
Described spacer center is welded with conducting magnetic column.
Described magneto-dependent sensor adopts Hall switch integrated device.
The present invention is compared with background technology, and the beneficial effect having is:
1. compared with the Cylindrical Gear Meter of same volume, when by same traffic, rotating speed is lower, the pressure loss can reduce fluid by flowmeter time; Reduce the pressure loss and can improve on the one hand system effectiveness, save the energy, contribute 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 outer rotor flank profil is and the partial arc flank profil of internal rotor conjugation that profile of tooth is simpler, compared with elliptic gear handling ease;
On outer rotor, can arrange multipair magnet steel, 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 the strength reduction of axis hole to upper and lower end cap, reduces upper and lower end cap deformation quantity under high pressure.
5, the advantage of maximum of the present invention is in the time that 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 reduce the pressure loss.
VS2 type gear meter in the VS Series Gear flowmeter that Wei Shi company of Germany produces is in the time being 100L/min by flow, rotating speed is 3600r/min left and right, and the of the present invention two-way cycloid rotor flowmeter identical with VS2 type gear meter overall volume be in the time being 100L/min by flow, rotating speed only has 500r/min.
Brief description of the drawings
Fig. 1 is the sectional structure schematic 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, in this figure, 2 pairs of magnet steel (i.e. 4 pieces of permanent-magnet steels 9) is set on outer rotor 4;
Fig. 3 is arrangement figure when 3 pairs of magnet steel (i.e. 6 pieces of permanent-magnet steels 9) are set on the outer rotor 4 in Fig. 1;
In Fig. 3: the schematic top plan view of outer rotor 4 during (a) for 3 pairs of magnet steel of layout; (b) vertical view of upper end cover 1 during for 3 pairs of magnet steel of layout;
Fig. 4 is arrangement figure when 4 pairs of magnet steel (i.e. 8 pieces of permanent-magnet steels 9) are set on the outer rotor 4 in Fig. 1;
In Fig. 4: the schematic top plan view of outer rotor 4 during (a) for 4 pairs of magnet steel of layout; (b) vertical view of upper end cover 1 during for 4 pairs of magnet steel of layout;
Fig. 5 is the schematic top plan view of the bottom end cover 3 in Fig. 1;
Fig. 6 is the elevational schematic view of the upper end cover 1 in Fig. 1;
Fig. 7 is two logical oil grooves (21,22) on the bottom end cover (3) in Fig. 1 a kind of embodiment figure in the time that internal rotor has 3 teeth, outer rotors to have 4 teeth;
Fig. 8 is two logical oil grooves (21,22) on the middle bottom end cover (3) in Fig. 1 a kind of embodiment figure in the time that internal rotor has 4 teeth, outer rotors to have 5 teeth;
Figure (a) and to scheme (b) be respectively the situation of inner and outer rotors while being positioned at the different position of engagement in Fig. 8.
Fig. 9 is the principle of work schematic diagram of Fig. 1;
Figure 10 is the enlarged diagram of X portion in Fig. 1.
Figure 11 is the schematic top plan view of internal rotor 5 in Fig. 1.
Figure 12 is the schematic top plan view of outer rotor 4 in Fig. 1.
In 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 sensors, 17. sensor apertures, 18. sensor apertures, 19. hydraulic fluid ports, 20. hydraulic fluid ports, 21. logical oil grooves, 22. logical oil grooves, 23. balancing slits, 24. balancing slits, 25. O-ring seals, 26. internal rotor balancing orifices 26, outer rotor balancing orifice 27.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described.
Embodiment 1, Fig. 1, Fig. 2, Fig. 5, Fig. 6, Fig. 7 and Figure 10 have provided a kind of high voltage-resistant bi-directional cycloid rotor flowmeter, comprise the high pressure resistant closed cavity being formed by upper end cover 1, toroidal cavity housing 2 and bottom end cover 3, in toroidal cavity housing 2, be provided with a rooted tooth wheel shaft 6, be supported in respectively in the axis hole of upper end cover 1 and bottom end cover 3, thereby make the two ends up and down of gear shaft 6 rely on transition fit realization to be connected with upper end cover 1 and bottom end cover 3 respectively.The internal rotor 5 of gerotor type is installed on gear shaft 6, and the number of teeth of internal rotor 5 is 3, and the tooth curve of internal rotor 5 is the equidistant curve of curtate epicycloid (belonging to routine techniques); The number of teeth of the outer rotor 4 matching with it is 4, and the flank profil of outer rotor 4 is and the partial arc flank profil of internal rotor 5 conjugation, thereby obtains the profile of tooth as described in Fig. 2 and 7.
Gear shaft 6 is sleeved in the inner chamber of internal rotor 5, and internal rotor 5 is sleeved in the inner chamber of outer rotor 4, and internal rotor 5 is rotatedly connected by bearing I 8 and gear shaft 6, and outer rotor 4 is rotatedly connected by bearing II 7 and toroidal cavity housing 2.Specific as follows:
Between internal rotor 5 and gear shaft 6, be connected by bearing I 8, 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 the outer rotors 4 that engage with it, and the outside of outer rotor 4 is that the bearing II 7(bearing II 7 being fixed on 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 bias, 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), the permanent-magnet steel assembly of 2 pairs 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 4,4 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 (, the N utmost point S of adjacent permanent-magnet steel 9 is extremely contrary).
On upper end cover 1, centered by outer rotor 4 revolving shaftes, become 30 ° to be provided with first sensor aperture 17 and the second sensor aperture 18(, 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, one piece of magneto-dependent sensor 16 of each layout on every spacer 15.
In the time that outer rotor 4 is permeability magnetic material, in the outside of permanent-magnet steel 9, cover has non-magnetic magnet steel cover 13, and magnet steel cover 13 and spacer 15 adopt non-magnetic stainless steel material to make.Magneto-dependent sensor 16 adopts Hall switch integrated device (the locking-typed Hall switch integrated device of the single output of ZH3070 series that for example can select Hangzhou Zhong Huo Electronics Co., Ltd. to produce).Upper end cover 1, toroidal cavity housing 2, bottom end cover 3, outer rotor 4 and internal rotor 5 adopt 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) center be welded with conducting magnetic column 21, this structure can obviously strengthen the magnetic induction density of magneto-dependent sensor 16 present positions.
On bottom end cover 3, be provided with oil storage tank I 21 and oil storage tank II 22, 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 eccentric throw line; Oil storage tank I 21 and oil storage tank II 22 symmetrical both sides that are positioned at 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 be all connected in all annular seal spaces of eccentric throw line homonymy with self, same, oil storage tank II 22 be all connected in all annular seal spaces of eccentric throw line homonymy with self.
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 taking the internal rotor centre of gyration as the center of circle, circular arc taking the root radius of internal rotor as radius, the outer rim of crescent shape oil groove be the centre of gyration taking outer rotor as the center of circle, the circular arc taking 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, conventionally 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 conventionally), and eccentric throw is large, and traditional crescent shape is no longer suitable for (can cause and cannot seal).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 (, oil storage tank I 21 and annular seal space that he is communicated with and the sealing of 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 and the oil storage tank II 22 shown in Fig. 7.
The shape of Fig. 7 two oil grooves (oil storage tank I 21 and oil storage tank II 22) that bottom end cover 3 is opened during for 3 teeth for internal rotor 5, oil storage tank I 21 and oil storage tank II 22 are symmetrical along eccentric throw line.Set forth as an example of oil storage tank I 21 example below:
Oil storage tank I 21 is mainly made up of 4 sections of circular arcs and 3 sections of straight lines.
These 4 sections of circular arcs are respectively:
Taking the centre of gyration of outer rotor 4 as the center of circle, and circular arc a taking the root radius of outer rotor 4 as radius,
Circular arc b taking internal rotor 5 centres of gyration as the center of circle, taking 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 of straight lines are respectively:
Connect straight line e, the f of circular arc b and circular arc c,
Connect the straight line g of 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 to rounding processing, whole oil groove can be processed by CNC milling machine.
Specifically do description below explanation:
There are 3 teeth for internal rotor 5, outer rotor 4 has the situation of 4 teeth, (what in reality, internal rotor 5 contacted with outer rotor 4 is a line to have 4 meshing points, 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.Tetra-points of ABCD shown in Fig. 7 are meshing point projections on upper end cover 1 in the time that outer rotor 4 and internal rotor 5 are on ad-hoc location.Illustrating of ad-hoc location: have 3 teeth for internal rotor 5, outer rotor 4 has the situation of 4 teeth, tetra-points of ABCD refer to when outer rotor 4 is when as shown in Figure 7 about the position of eccentric throw line symmetry, four meshing points projected position on upper end cover 1, there are 4 teeth for internal rotor 5, outer rotor 4 has the situation of 5 teeth, described tetra-points of ABCD do not occur at synchronization, wherein 2 of AB are for when outer rotor 4 is when as shown in Figure 8 (a) about the position of eccentric throw line symmetry, be positioned at the subpoint of two meshing points of upper end cover 1 projection the first half, 2 of CD are when outer rotor 4 is 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, 36 ° of (or clockwise) rotations counterclockwise) after, be positioned at the subpoint of two meshing points of upper end cover 1 projection the latter half, as shown in Figure 8 (b) shows.
If heavy line in Fig. 7 is the movement locus of any meshing point in the time that internal rotor 5, outer rotor 4 rotate, this track can draw by the motion of computer simulation inner and outer rotors.
Straight line e met the point of A shown in Fig. 7, and was tangential on 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 meet the upper any point of small arc-shaped c in Fig. 7 when outer rotor 4 position the distance of the drop shadow curve of outer rotor 4 inside surfaces on upper end cover 1 be greater than 3mm, and straight line e and small arc-shaped c be except A point, can not with in Fig. 7 when outer rotor 4 position the drop shadow curve of outer rotor 4 inside surfaces on upper end cover 1 crossing.
Straight line g and small arc-shaped d are as shown in Figure 7, should meet small arc-shaped d and cross the point of C shown in Fig. 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 in Fig. 7), and straight line g, small arc-shaped d and any point that connects on their arc transition line are greater than 1mm apart from the distance of any point on the inner small arc-shaped curve of path of action line (heavy line in Fig. 7).
Meshing point A shown in straight line f connection layout 7 and circular curve c(joining place rounding), it should meet whole section of straight line and is all 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 Fig. 7, and straight line f is upper except being greater than 3mm with other any points interior point to the distance of any point in the drop shadow curve of internal rotor 5 outside surfaces on upper end cover 1 in the time that internal rotor 5 is positioned at position shown in Fig. 7 apart from meshing point A 3mm.
In this example, the radius of small arc-shaped c is 5mm, and the radius of small arc-shaped d is 2mm.
On bottom end cover 3, be respectively equipped with logical hydraulic fluid port I 19 and logical hydraulic fluid port II 20, 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.
Remarks explanation: logical hydraulic fluid port I 19, logical hydraulic fluid port II 20 are as oil-in and oil-out; In the time of oil-in and oil-out exchange, internal rotor 5 changes sense of rotation with outer rotor 4 simultaneously.
On upper end cover 1, be provided with and oil storage tank I 21 and oil storage tank II 22 positive corresponding equal pressure oil groove I 23 and equal pressure oil groove II 24 one by one mutually,, all the shape of cross section of pressure oil groove I 23 is completely with oil storage tank I 21, and all the shape of cross section of pressure oil groove II 24 is completely with oil storage tank II 22.All the degree of depth of pressure oil groove I 23 and equal pressure oil groove II 24 is only all 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 inner and outer rotors axially loaded imbalance.
Internal rotor 5 is provided with the internal rotor balancing orifice 26 that longitudinally runs through internal rotor 5, outer rotor 4 is provided with the outer rotor balancing orifice 27 that longitudinally runs through outer rotor 4, the aperture of described internal rotor balancing orifice 26 and outer rotor balancing orifice 27 is 0.5 ~ 1mm(, and aperture is not to affect oil suction chamber and to go out the sealing between oil pocket and can make fluid by being advisable).
Although, upper end cover 1 is provided with and oil storage tank I 21 and oil storage tank II 22 positive corresponding equal pressure oil groove I 23 and equal pressure oil groove II 24 one by one mutually, but when internal rotor 5 and outer rotor 4 produce while being offset play up and down, due to 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 internal rotor balancing orifice 26 that the present invention arranges on internal rotor 5 and the outer rotor balancing orifice 27 arranging on 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, contribute to reduce the end-face friction of internal rotor 5 and outer rotor 4.
As shown in Figure 9, the course of work is specific as follows for the principle of work of high voltage-resistant bi-directional cycloid rotor flowmeter of the present invention:
Its core parts are that (eccentric throw is cycloidal gear e) engaging to a pair of bias, the number of teeth of its outer rotor 4
than the number of teeth of internal rotor 5
many 1, in engagement rotation process, can form
individual independently sealed volume is (in the time having 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 in the time having odd number cavity volume, along with the rotation of inner and outer rotors, the sealed volume being connected with one of them oil storage tank is
individual (or
individual), and with the sealed volume that another oil storage tank is connected be
individual (or
individual)), along with the rotation of internal rotor 5 and outer rotor 4, the volume of each sealed volume constantly changes.In the time that flowmeter right side dotted line oil groove is oil feed groove (when left-hand broken line oil groove is oil feed groove, situation is contrary therewith), in the sealed volume of two, right side, oil liquid pressure is greater than the pressure of two sealed volumes in left side.It is large that two, right side sealed volume constantly becomes under pressure, is all rotated counterclockwise thereby promote inner and outer rotors.
Remarks explanation: in rotary course, cavity volume number is constant, just certain cavity volume can become very little sometimes.
The process that in Fig. 9, (a) enters flowmeter A chamber to (d) for fluid, and (d) process for fluid outflow flowmeter A chamber to (f).As shown in (a) in Fig. 9, now A chamber volume minimum; Internal rotor 5 and outer rotor 4, under the effect of right atrial pressure oil, are rotated counterclockwise simultaneously, and internal rotor 5 rotating speeds are very fast, and outer rotor 4 rotating speeds are slower.In the time forwarding position shown in (b) to, A chamber volume expands, and in the time forwarding (c) position to, A chamber volume further expands.Along with the continuous expansion of A chamber volume, fluid constantly enters flowmeter, among A chamber.In the time arriving (d) position, A chamber volume maximum, the process that fluid enters flowmeter finishes.Internal rotor 5 and outer rotor 4 continue motion afterwards, arrive (e) position, and now A chamber volume starts to reduce, and the fluid in A chamber is forced out from going out oil groove of left side, and in the time forwarding (f) position to, it is minimum that A chamber volume reaches, and oil extraction process finishes.
In the course of the work, a tooth of outer rotor 4 turns over one week to this flowmeter, completes a working cycle completing, and realizes fluid and enters flowmeter and extrude flowmeter process once.For the outer rotor 4 that has n tooth, often turn around, will there is n the working cycle identical with A chamber.For example in diagram, have the outer rotor of 4 teeth to rotate a circle, flowmeter can pass through 4 times of volumes in the time of the maximum of A chamber
liquid.So, fluid just can continuously enter flowmeter from oil feed groove, and is split into liquid piece one by one, is more constantly forced out flowmeter.
When actual use, if when 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 is connected with flowline (oil inlet pipe) with extraneous oil inlet pipe (flowline) 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 leading to hydraulic fluid port I 19, and then enter into the closed containing cavity that upper end cover 1 and bottom end cover 3 and toroidal cavity housing 2 form, further promoting internal rotor 5 and outer rotor 4 rotates, fluid is divided, and finally enter in 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 is led to hydraulic fluid port I 19 for oil-out for oil-in, fluid flow process is contrary with said process.
When internal rotor 5 and outer rotor 4 rotate, the correspondingly sensitizing range of inswept magneto-dependent sensor 16 of the permanent-magnet steel 9 that outer rotor 4 is embedded in, makes magneto-dependent sensor 16 sense the variation of permanent magnetic field, changes output signal level.This signal is transported in secondary instrument, thereby obtains the concrete flow (this is with existing routine techniques) of fluid.From the theory of engagement of cycloid internal gear, in the time that flow keeps invariable, the angular velocity of interior outer rotor changes.But for having the outer rotor of 4 teeth, rotate the fluctuation of speed within one week four times, therefore in the time only having a pair of or two pairs of permanent-magnet steels 9, can be by permanent-magnet steel 9 being circumferentially uniformly distributed along outer rotor 4, only have in the time of outer rotor 4 Rotate 180s ° or 90 ° and could act on a magneto-dependent sensor 16 wherein, in the time of constant flow, the square-wave signal that magneto-dependent sensor 16 is exported is also constant, and square wave frequency be directly proportional to the fluid flow by flowmeter (measure by secondary instrument the square wave number that magneto-dependent sensor 16 exports and can obtain the flow information by flowmeter), now the aperture that magneto-dependent sensor 16 is housed on upper end cover 1 (, first sensor aperture 17 and the second sensor aperture 18) position do not need particular design yet, can be at an arbitrary position, as long as ensure that permanent magnet can inswept this region.
Embodiment 2, by the number of teeth of the internal rotor in embodiment 15 serve as reasons " 3 " make " 4 " into, make the number of teeth of outer rotor 4 into " 5 " by " 4 ", internal rotor 5 tooth curves remain the equidistant curve of curtate epicycloid; The flank profil of outer rotor 4 remains the partial arc flank profil with internal rotor 5 conjugation; All the other are with embodiment 1.
The shape (its shape and feature are equal to oil storage tank I 21 and the oil storage tank II 22 in embodiment 1) of Fig. 8 two oil grooves that bottom end cover 3 is opened during for 4 teeth for internal rotor 5.
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 taking outer rotor 4 revolving shaftes as the center of circle (this radius of a circle can arbitrarily be got according to actual needs).First suppose outer rotor 4 be positioned at shown in Fig. 8 (a) about the axisymmetric position of bias, and this position is made as to 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 for example, according to the instantaneous delivery formula of cycloid internally meshed rotor (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 time, by knowing that to instantaneous delivery integration outer rotor 4 turns over when arbitrarily angled by the fluid volume of flowmeter.Suppose to arrange that n is to magnet steel, only need make flowmeter outer rotor 4 turn over certain angle
, make turning over this angle
time, by flowmeter fluid volume when the fluid volume by flowmeter just in time turns a whole circle for outer rotor 4
.Second piece of magnet steel becomes centered by outer rotor 4 revolving shaftes with first piece of magnet steel
degree angle.Computing method for the magnet steel position such as the 3rd piece, the 4th piece are identical identical with second piece, by that analogy.
Embodiment 3, make the quantity of the permanent-magnet steel assembly in embodiment 1 into " 3 pairs " by " 2 pairs ", all the other are with embodiment 1.The arrangement mode of the arrangement mode of 6 permanent-magnet steels 9 and first sensor aperture 17 and the second sensor aperture 18 as shown in Figure 3.Concrete arrangement mode calculates with reference to the set-up mode in embodiment 2.
Embodiment 4, make the quantity of the permanent-magnet steel assembly in embodiment 1 into " 4 pairs " by " 2 pairs ", all the other are with embodiment 1.The arrangement mode of the arrangement mode of 8 permanent-magnet steels 9 and first sensor aperture 17 and the second sensor aperture 18 as shown in Figure 4.Concrete arrangement mode calculates with reference to the set-up mode in embodiment 2.
Embodiment 5, in the time of unnecessary 4 of the number of teeth of internal rotor 5, now the arrangement mode of permanent-magnet steel 9 calculates with reference to the set-up mode in embodiment 2.Just the shape of oil storage tank I 21 and oil storage tank II 22 no longer meets the feature in embodiment 1, and be changed to the shape (this crescent has been widely used in gerotor pump, for example, according to the related content of the cycloid gear pump in He Cunxing " Hydraulic Elements ") of common gerotor pump crescent.
Claims (8)
1. high voltage-resistant bi-directional cycloid rotor flowmeter, it is characterized in that: comprise the high pressure resistant closed cavity being formed by upper end cover (1), toroidal cavity housing (2) and bottom end cover (3), in described toroidal cavity housing (2), be provided with gear shaft (6), intermeshing internal rotor (5) and outer rotor (4), the two ends up and down of described gear shaft (6) rely on transition fit realization to be connected 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 bias, and internal rotor (5) outer wall rotating in the inner chamber of outer rotor (4) and outer rotor (4) inwall form the annular seal space that several volumes cycle changes;
On the upper surface of outer rotor (4), centered by outer rotor (4) revolving shaft, the permanent-magnet steel assembly of 1～4 pair is set, 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 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), in first sensor aperture (17) and the second sensor aperture (18), be provided with separately high pressure resistant, a non-magnetic spacer (15), the upper one piece of magneto-dependent sensor (16) of arranging of described every spacer (15);
On bottom end cover (3), be provided with oil storage tank I (21) and oil storage tank II (22), 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 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; The annular seal space that several volume cycles that described internal rotor (5) outer wall forms with outer rotor (4) inwall change is connected with any one in oil storage tank I (21) and oil storage tank II (22);
On bottom end cover (3), be respectively equipped with logical hydraulic fluid port I (19) and logical hydraulic fluid port II (20), 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);
On upper end cover (1), be provided with and oil storage tank I (21) and oil storage tank II (22) all pressure oil groove I (23) and equal pressure oil groove II (24) one to one mutually, thereby guarantee the axially loaded balance of internal rotor (5) and outer rotor (4);
The number of teeth many 1 of the gear ratio internal rotor (5) of described outer rotor (4).
2. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 1, is characterized in that:
In the time that outer rotor (4) quantity that is 4 teeth and permanent-magnet steel assembly is 1 pair or 2 pairs, 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 upper end cover (1) centered by outer rotor (4) revolving shaft.
3. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 2, is characterized in that:
Described oil storage tank I (21) and oil storage tank II (22) are symmetrically located at the both sides of eccentric throw line;
The number of teeth=3 o'clock of internal rotor (5), described oil storage tank I (21) is made up of 4 sections of circular arcs and 3 sections of straight lines;
These 4 sections of circular arcs are respectively:
Taking the centre of gyration of outer rotor (4) as the center of circle, the circular arc a taking the root radius of outer rotor (4) as radius;
Taking the centre of gyration of internal rotor (5) as the center of circle, the circular arc b taking the root radius of internal rotor (5) as radius;
Oil groove top small arc-shaped c, described oil groove top small arc-shaped c should, as far as possible near the tooth top edge of outer rotor (4), still can not exceed 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 of straight lines are respectively:
The straight line e and the straight line f that connect successively circular arc c and circular arc b, straight line e and straight line f intersect at another meshing point A;
Connect the straight line g of circular arc b and circular arc d.
4. high voltage-resistant bi-directional cycloid rotor flowmeter according to claim 3, is characterized in that: on upper end cover (1), have two with oil storage tank I (21) on bottom end cover (3) and oil storage tank II (22) positive corresponding equal pressure oil groove I (23) and equal pressure oil groove II (24) one by one mutually; Described equal pressure oil groove I (23) and all pressure oil groove II (24) are for guaranteeing the axially loaded balance of internal rotor (5) and outer rotor (4);
The degree of depth of described equal pressure oil 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 longitudinally runs through internal rotor (5), outer rotor (4) is provided with the outer rotor balancing orifice (27) that longitudinally 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 of circular arcs in oil storage tank I (21) and the acute angle of 3 sections of straight line joints all carry out rounding processing, and whole oil groove can be processed by 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).
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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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| 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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| CN102914338B true CN102914338B (en) | 2014-08-13 |
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Families Citing this family (6)
| 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 |
| CN104949716B (en) * | 2015-06-18 | 2017-10-24 | 合肥精特仪表有限公司 | A kind of corrosion-resistant small-pulse effect equivalent flow meter |
| 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 |
| 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 |
| 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 |
| DE102019001466B4 (en) * | 2019-03-04 | 2020-10-15 | Alexander Leonhardt | Dosing measuring sensor |
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| EP2275678A1 (en) * | 2009-07-13 | 2011-01-19 | Sensile Pat AG | Pump with rotor position measurement system |
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|---|---|---|---|---|
| CN2239017Y (en) * | 1995-05-09 | 1996-10-30 | 赵汝沅 | Rotor volume flowmeter |
| CN2307283Y (en) * | 1996-10-26 | 1999-02-10 | 杜召景 | Displacement antijam Roots type flowmeter |
| CN1680788A (en) * | 2004-04-09 | 2005-10-12 | 兰州科庆仪器仪表有限责任公司 | Flowmeter with movable annular rotor |
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| EP2275678A1 (en) * | 2009-07-13 | 2011-01-19 | Sensile Pat AG | Pump with rotor position measurement system |
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