CN202946371U - Internal gear pump - Google Patents
Internal gear pump Download PDFInfo
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- CN202946371U CN202946371U CN 201220434863 CN201220434863U CN202946371U CN 202946371 U CN202946371 U CN 202946371U CN 201220434863 CN201220434863 CN 201220434863 CN 201220434863 U CN201220434863 U CN 201220434863U CN 202946371 U CN202946371 U CN 202946371U
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Abstract
The utility model provides an internal gear pump capable of reducing the noise. The internal gear pump comprises an inner rotor (2a) and an outer rotor (2b), wherein the inner rotor (2a) is fixedly arranged on a driving shaft (a shaft (30)) which freely rotates and is supported by a bearing (a bearing part (41)) arranged on a shell (4), and the inner rotor (2a) is provided with outer teeth; and the outer rotor (2b) is arranged in a pump containing hole (400) formed in the shell (4) in a free embedding state, and the outer rotor (2b) is provided with inner teeth and is meshed with the inner rotor (2a), at least one part of a tooth surface (21) of the inner rotor (2a) is provided with a first angle (phi i) larger than zero relative to a shaft of the inner rotor (2a), and the distance between the at least one part of the tooth surface of the inner rotor and the axial center of the inner rotor (2a) is gradually reduced from a bearing side (a side in a negative direction of an x-axis) to an opposite side of the bearing (a side in a positive direction of the x-axis).
Description
Technical field
The utility model relates to a kind of crescent gear pump.
Background technique
All the time, known have a kind of crescent gear pump, comprising: the internal rotor with external tooth; The external rotor that has internal tooth and mesh with internal rotor.For example to be fixed on internal rotor by the bearing supporting be on rotation live axle freely to the pump of patent documentation 1 record.
[formerly technical paper]
[patent documentation]
[patent documentation 1] TOHKEMY 2007-255341 communique
Yet in the pump of patent documentation 1 record, when internal rotor tilted, internal rotor and external rotor were interfered and may be produced noise.The purpose of this utility model is to provide a kind of crescent gear pump that can reduce noise.
The model utility content
To achieve these goals, pump of the present utility model preferably, at least a portion of the flank of tooth of internal rotor along with from the bearing side towards the distance apart from the axle center of internal rotor shortens gradually with the bearing opposition side.
First aspect of the present utility model provides a kind of crescent gear pump, it is characterized in that, possesses: internal rotor, and it is fixed on by the bearing supporting that is arranged at shell is on rotation live axle freely, and has external tooth; External rotor, it is arranged in the pump accepting hole that is formed at described shell with trip embedding state, have internal tooth and mesh with described internal rotor, at least a portion of the flank of tooth of described internal rotor has with respect to the axle of described internal rotor than zero the first large angle, and along with shortening gradually apart from the distance in the axle center of described internal rotor from described bearing side towards the opposition side of described bearing.
On the basis of the crescent gear pump of first aspect, it is characterized in that, at least a portion of the flank of tooth of described external rotor has with respect to the axle of described external rotor than zero the second large angle, and along with shortening gradually apart from the distance in the axle center of described external rotor from described bearing side towards the opposition side of described bearing.
On the basis of the crescent gear pump of second aspect, it is characterized in that, the flank of tooth of described internal rotor has described the first angle on the whole circumference of described internal rotor, described the first angle is constant on the whole circumference of described internal rotor, the flank of tooth of described external rotor has described the second angle on the whole circumference of described external rotor, described the second angle is constant and equate with described the first angle on the whole circumference of described external rotor.
On the basis of the crescent gear pump of second aspect, it is characterized in that, the flank of tooth of described internal rotor is in the regulation zone of tooth top side, along with from the tooth bottom side towards the tooth top side and described the first angle reduces, the flank of tooth of described external rotor in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and described the second angle reduces.
On the basis of the crescent gear pump of fourth aspect, it is characterized in that, the flank of tooth of the tooth top of described internal rotor is zero with respect to the axle angulation of described internal rotor, the flank of tooth at the bottom of the tooth of described external rotor is zero with respect to the axle angulation of described external rotor.
On the basis of the crescent gear pump of second aspect, it is characterized in that, the flank of tooth of described internal rotor is in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and described the first angle reduces, the flank of tooth of described external rotor in the regulation zone of tooth top side, along with from the tooth bottom side towards the tooth top side and described the second angle reduces.
On the basis of the crescent gear pump aspect the 6th, it is characterized in that, the flank of tooth at the bottom of the tooth of described internal rotor is zero with respect to the axle angulation of described internal rotor, the flank of tooth of the tooth top of described external rotor is zero with respect to the axle angulation of described external rotor.
On the basis of the crescent gear pump of first aspect, it is characterized in that, the profile of tooth of described internal rotor and described external rotor is the trochoid profile of tooth.
On the basis of the crescent gear pump of eight aspect, it is characterized in that, the parameter of the profile of tooth of described internal rotor and described external rotor is Base radius and creation circular diameter axially gradually changing along described internal rotor and described external rotor, along with from the opposition side of described bearing side towards described bearing, the creation circular diameter of described internal rotor increases gradually and Base radius reduces gradually, along with from the opposition side of described bearing side towards described bearing, the creation circular diameter of described external rotor increases gradually and Base radius reduces gradually.
On the basis of the crescent gear pump aspect the 9th, it is characterized in that, the tooth top of described internal rotor and the flank of tooth at the bottom of tooth are zero with respect to the axle angulation of described internal rotor, and the tooth top of described external rotor and the flank of tooth at the bottom of tooth are zero with respect to the axle angulation of described external rotor.
[model utility effect]
Thus, can suppress the inclination of internal rotor and reduce noise.
Description of drawings
Fig. 1 is the axial sectional view of embodiment 1 the pump that is arranged at case of transmission.
Fig. 2 is the axial plan view of embodiment 1 pump section.
Fig. 3 is that the A-A of Fig. 2 looks sectional view.
Fig. 4 is (a) stereogram and (b) plan view of embodiment 1 internal rotor.
Fig. 5 is (a) stereogram and (b) plan view of embodiment 1 external rotor.
Fig. 6 is the plan view observed from the opposition side of bearing portion of (a) of embodiment 1 the state that is provided with internal rotor on external rotor and the plan view of (b) observing from the bearing portion side.
Fig. 7 is the axial sectional view in embodiment 1 the work of pump section.
Fig. 8 is the axial sectional view in the work of pump section of comparative example.
Fig. 9 is (a) stereogram and (b) plan view of embodiment 2 internal rotor.
Figure 10 is (a) stereogram and (b) plan view of embodiment 2 external rotor.
Figure 11 is the plan view observed from the opposition side of bearing portion of (a) of embodiment 2 the state that is provided with internal rotor on external rotor and the plan view of (b) observing from the bearing portion side.
Symbol description:
Embodiment
Below, based on accompanying drawing, the mode that realizes crescent gear pump of the present utility model is described.
[embodiment 1]
Embodiment 1 pump 1 is by electric motor driven motor-drive pump, is applicable to the hydraulic equipment of vehicle.Particularly, pump 1 is the auxiliary motor-drive pump of automatic transmission (CVT) use that is equipped on vehicle (Motor Vehicle), sucks the oil (CVTF) of cooling use of ejection automatic transmission (CVT) as fluid.Fig. 1 is that the pump 1 that will be arranged at case of transmission 100 utilizes the sectional view that dissects by the plane in its axle center.Suck and represented by arrow from the flowing of oil that pump 1 sprays to pump 1.For convenience of explanation, the direction of extending along the axle center (axle 30) of pump 1 arranges the x axle, with respect to motor part 3, with pump section 2 sides as postive direction.
Case of transmission 100 is shells of automatic transmission, is formed with the chimeric recess that the round-ended cylinder shape is arranged 101 that pump 1 is set.Not shown suction oil circuit is to recess 101 openings, and the ejection oil circuit 102 that is connected with the blowing unit 45 of pump 1 is to the bottom opening of recess 101.Pump 1 has: the pump section 2 that sucks ejection oil; The motor part 3 of driven pump section 2 rotations; Accommodate the shell 4 that pump section 2 and motor part 3 are set.
Shell 4 has the first shell 4a and second housing 4b.The first shell 4a has: possessing in interior all sides has the pump of the pump of round-ended cylinder shape accepting hole 400 accommodation section 40; Give prominence to the axial opposed side (x axle negative direction side) of pump accepting hole 400 from the bottom of pump accepting hole 400 with pump accommodation section 40 settings integratedly, and possess the bearing portion 41 of axle accepting hole 410 in interior all sides; Be arranged at integratedly the bottom of pump accommodation section 40 in the opposed mode of outer circumferential face across radial clearance and bearing portion 41, and possess the motor accommodation section 42 of stator accepting hole 420 in interior all sides; Be arranged on integratedly the lip part 43 on the axial end portion (x axle negative direction end) of motor accommodation section 42 in the mode of outward radial expansion.In the pump accommodation section 40 and be provided with suction port 401 and the ejiction opening 402 of groove shape in the bottom of pump accepting hole 400.Second housing 4b comprises the sucting 44 that is formed through suction oil circuit 440 and the blowing unit 45 that is formed through ejection oil circuit 450.Be formed with in second housing 4b and mating face that the first shell 4a engages end recess 460 is arranged.
The internally meshed type gear pump (crescent gear pump) that pump section 2 is gear pumps, specifically quietness is higher is to have internal rotor 2a and external rotor 2b as the pump structure body of pump rotor.Internal rotor 2a is the external tooth gear with n (being in an embodiment 6) number of teeth, and all sides are provided with axle hole 20 is set within it.The chimeric axle that is arranged in an end (x axle postive direction end) as the axle 30 of live axle of pump section 2 (internal rotor 2a) arranges hole 20, thereby is fixed in internal rotor 2a.The profile of tooth of internal rotor 2a is the trochoid profile of tooth.External rotor 2b is the internal-gear with n+1 (being in an embodiment 7) number of teeth.External rotor 2b accommodates freely with trip embedding state, rotation and is arranged in pump accommodation section 40 (the pump accepting holes 400) that are formed at the first shell 4a.The central shaft of the outer circumferential face of external rotor 2b and external rotor 2b (x axle) almost parallel ground arranges, and with respect to the inner peripheral surface of the pump accepting hole 400 of axle (x axle) the almost parallel ground setting of axle accepting hole 410, separate radially small gap and opposed.The profile of tooth of external rotor 2b is the trochoid profile of tooth.Second housing 4b arranges in the mode that the x axle postive direction end face with the first shell 4a of pump accepting hole 400 openings covers, and bolton is in the first shell 4a.The suction regional connectivity of the suction oil circuit 440 of second housing 4b and pump section 2, the ejection regional connectivity of ejection oil circuit 450 and pump section 2.
Motor part 3 is the brushless DC motors that are made of rotor part 3a and stator department 3b.The rotor core 32 as yoke section that rotor part 3a has axle 30, magnet 31, their are linked.Magnet 31 is permanent magnet cylindraceous (ring magnets), is upwards to have the field magnet of a plurality of magnetic poles in week.Rotor core 32 is magnetic, is formed by the Ferrious material material.Rotor core 32 has a round-ended cylinder shape for what be provided with recess 320 in interior all sides, has been formed through axle in its bottom hole 321 is set.Be formed with magnet at the outer circumferential side of rotor core 32 section 322 is set.By the bonding magnet 31 of section 322 is set at magnet, and magnet 31 is fixedly installed on rotor core 32.Stator department 3b has as the stator 33 of excitation mechanism and coil 34.Stator 33 has stator core and insulator (insulator) 331.Be wound with winding coil 34 across insulator 331 on each tooth 330 of stator core.By to coil 34 energising, and stator 33 produces magnetic field, thereby drives rotor part 3a rotation.
As described above, contain the chimeric recess 101 that is arranged on case of transmission 100 of shell 4 of pump section 2 and motor part 3.The chimeric ejection oil circuit 102 that is arranged on case of transmission 100 of the blowing unit 45 of second housing 4b.The lip part 43 of shell 4 with the mode bolton of surrounding recess 101 in case of transmission 100.Need to prove, cover 4c bolton is in lip part 43, and the opening of the motor accommodation section 42 of shell 4 is inaccessible, thereby guarantees the tightness in motor accommodation section 42.Gap between the inner peripheral surface of the outer circumferential face of shell 4 and case of transmission 100 (recess 101) (fill with oil sucting) 103 is by the sealing component 104 on the opening portion that is arranged on recess 101, cuts off and being communicated with of the outside of automatic transmission.And above-mentioned gap (fill with oil sucting) 103 cut off and sprays being communicated with of oil circuit 102 by the sealing component 105 between the outer circumferential face that is arranged on blowing unit 45 and the inner peripheral surface that sprays oil circuit 102.
Fig. 2 has removed to observe the plan view of pump section 2 from an axial side (x axle postive direction side) under the state of second housing 4b.Fig. 3 is the figure that the A-A that schematically shows Fig. 2 looks section.For convenience of explanation, the y axle of the axle center O by internal rotor 2a (axle 30) and the z axle of quadrature with it are set.The sense of rotation of internal rotor 2a and external rotor 2b as shown by arrows.Internal rotor 2a is arranged on interior all sides of external rotor 2b in the mode with external rotor 2b engagement.External rotor 2b is by the rotation of internal rotor 2a, and with the position of internal rotor 2a engagement on driven rotation.The zone that surrounds at the inner peripheral surface by the tooth of the inner peripheral surface of the tooth of intermeshing internal rotor 2a and external rotor 2b forms pump chamber r, the number of teeth with internal rotor 2a is set with counting (amounting to 6) pump chamber r1～r6., compare with the z axle during along the direction rotation of the arrow of Fig. 2 as internal rotor 2a, the volume of the pump chamber r1～r3 of y axle postive direction side enlarges, and compares with the z axle, and the volume of the pump chamber r4～r6 of y axle negative direction side dwindles.Compare with the z axle, the zone of y axle postive direction side is for sucking the zone.The suction port 401 of the first shell 4a is arranged to crescent shape under observing from the x axle direction, so that the pump chamber r1～r3 regional with being present in suction is communicated with.And, the suction oil circuit 440 of second housing 4b and suction regional connectivity.Compare with the z axle, the zone of y axle negative direction side is the ejection zone.The ejiction opening 402 of the first shell 4a is arranged to crescent shape under observing from the x axle direction, so that the pump chamber r4～r6 regional with being present in ejection is communicated with.And, the ejection oil circuit 450 of second housing 4b and ejection regional connectivity.Pump section 2 is by making two rotor 2a, 2b rotation, and the oil that sucting (be present in suck zone pump chamber r) is sucked is from blowing unit (the pump chamber r that is present in the ejection zone) ejection.
Fig. 4 is internal rotor 2a (a) stereogram and the plan view of (b) observing from x axle postive direction side.Fig. 5 is external rotor 2b (a) stereogram and the plan view of (b) observing from x axle negative direction side.Fig. 6 is that the interior all sides at external rotor 2b arrange internal rotor 2a, the plan view of (a) observing from x axle postive direction side and the plan view of (b) observing from x axle negative direction side.The flank of tooth 21 of internal rotor 2a has with respect to the axle of internal rotor 2a than zero large angle θ i (with reference to Fig. 3), along with from the end face of the internal rotor 2a of bearing portion 41 sides (x axle negative direction side) towards with the end face of the internal rotor 2a of bearing portion 41 opposition sides (x axle postive direction side), and the distance from the axle center of internal rotor 2a to the flank of tooth 21 shortens gradually.That is, the flank of tooth 21 is arranged to along with towards x axle negative direction and gradually to the cone-shaped of outside diameter (side of leaving from the axle center) expansion.Taper is arranged at the integral body of the flank of tooth 21.The cross section in the axle center by internal rotor 2a becomes the trapezoidal shape that the bottom broadens as shown in Figure 3.The taper of the flank of tooth 21 is even with respect to direction (x axle direction) angulation (cone angle θ i) (gamut of the direction that pivots) on the whole circumference of internal rotor 2a of the axle extension of internal rotor 2a.In other words, the flank of tooth 21 has angle θ i on the whole circumference of internal rotor 2a, and θ i is constant on the whole circumference of internal rotor 2a.
The flank of tooth 22 of external rotor 2b has with respect to the axle of external rotor 2b than zero large angle θ o (with reference to Fig. 3), along with from the end face of the external rotor 2b of bearing portion 41 sides (x axle negative direction side) towards with the end face of the external rotor 2b of bearing portion 41 opposition sides (x axle postive direction side), and the distance from the axle center of external rotor 2b to the flank of tooth 22 shortens gradually.That is, the flank of tooth 22 is arranged to the cone-shaped that broadens to outside diameter (side of leaving from the axle center) gradually along with towards x axle negative direction.Taper is arranged on the integral body of the flank of tooth 22.The cross section in the axle center by external rotor 2b becomes trapezoidal shape as shown in Figure 3.The taper of the flank of tooth 22 is even on the whole circumference of external rotor 2b with respect to direction (x axle direction) angulation (cone angle θ o) of the axle extension of external rotor 2b.In other words, the flank of tooth 22 has angle θ o on the whole circumference of external rotor 2b, and θ o is constant on the whole circumference of external rotor 2b.Θ o set for θ i about equally.
[embodiment 1 effect]
Next, the effect of pump 1 is described.Fig. 7 and Fig. 8 are the sectional views same with Fig. 3, and the power that flows and act on internal rotor 2a of the oil of the pump section 2 in work as shown by arrows.Fig. 7 represents embodiment 1, and Fig. 8 represents comparative example.Comparative example and embodiment's 1 difference is that the flank of tooth 22 at the flank of tooth 21 of internal rotor 2a and external rotor 2b does not arrange taper and the flank of tooth 21,22 and the point of the axle almost parallel of rotor, and other points are identical with embodiment 1.
As shown in Figure 8, in the work of pump section 2, on the suction zone of y axle postive direction side, suck and press the flank of tooth 21 that acts on internal rotor 2a, and on the ejection zone of y axle negative direction side, the flank of tooth 21 that acts on internal rotor 2a is pressed in ejection.That is, the pressure of the pump chamber r in the pressure of the pump chamber r of internal rotor 2a by sucking the zone and ejection zone bears the load of radial direction (square with the axis Vertical direction).Particularly, internal rotor 2a presses (negative pressure) to bear to the load F1 of y axle postive direction effect by sucking sucking on the zone, presses by ejection on the ejection zone and bears to the load F2 of y axle postive direction effect.Need to prove, usually cut down output living load F2 greater than the living load F1 that cut down output by suction by ejection.Described load F1, F2 all act on internal rotor 2a to y axle postive direction.By described load F1, F2, the end P that produces x axle postive direction side take bearing portion 41 (pump section 2 side) wants to make internal rotor 2a along the right handed rotating force (the moment M1 of the first power) of Fig. 8 as fulcrum.On the other hand, drive the axle 30 of internal rotor 2a by bearing portion 41 single armed supportings.And, between axle 30 and axle accepting hole 410, and internal rotor 2a and shell 4 between have the gap of stipulating.Thus, by the moment M1 of the first power, the clockwise direction along Fig. 8 slightly rotates take end P as fulcrum to make internal rotor 2a, with respect to the axle center of axle accepting hole 410 and pump accepting hole 400 (external rotor 2b) and tilt (lying down).Thus, near the axial end of two rotor 2a, 2b, the flank of tooth of two rotor 2a, 2b is closer to each other, and the between cog minimum clearance (tip clearance) of two rotor 2a, 2b becomes too small, and the tooth of two rotor 2a, 2b interferes each other.Because this interference (toe joint touches) produces noise (beating dental).And in motor part 3 sides, the air gap because axle 30 tilts between rotor part 3a and stator department 3b produces deflection, thereby motor part 3 possibly can't be worked swimmingly.
With respect to this, in embodiment 1 pump section 2, the flank of tooth 21 of internal rotor 2a has cone angle θ i (with reference to Fig. 3), along with from bearing portion 41 sides (x axle negative direction side) towards with bearing portion 41 opposition sides (x axle postive direction side), and the distance from the axle center of internal rotor 2a to the flank of tooth 21 shortens gradually.Conical in shape due to this flank of tooth 21, as shown in Figure 7, under the effect of the pressure of the pump chamber r in the pressure of the pump chamber r that sucks the zone and ejection zone, not only the load F3 of the load F1 of radial direction, F2 but also thrust direction, F4 also act on internal rotor 2a (be decomposed into F1, F3 in the load that sucks the zone effect, be decomposed into F2, F4 in the load that sprays the zone effect).Particularly, internal rotor 2a is sucking the zone because suction is pressed (negative pressure) and also bears to the load F3 of x axle postive direction effect except load F1, spraying the zone due to the ejection pressure and also bearing except load F2 to the load F4 of x axle negative direction effect.Need to prove, cut down output living load F4 greater than the living load F3 that cut down output by suction by ejection.Described load F3, F4 are across end P and acting in opposition.By described load F3, F4, produce and want to make internal rotor 2a along the rotating force (the moment M2 of the second power) of the counter clockwise direction rotation of Fig. 7 take end P as fulcrum.Need to prove, when the cone angle θ i of the flank of tooth 21 of internal rotor 2a is larger or the scope of taper is set when wider, the size of load F3, the F4 i.e. size of the moment M2 of the second power is larger.The moment M2 of this second power is to the opposite direction effect of the moment M1 of the first power.Thus, compare with comparative example, the moment M1 of the first power reduces.Therefore, can suppress the inclination (lying down) of internal rotor 2a.Thus, the situation that the flank of tooth of inhibition internal rotor 2a and the flank of tooth of external rotor 2b interfere touches thereby reduce toe joint the noise (beating dental) that causes.And, increase that can contaminant restraining and improve the durability of pump section 2.
Need to prove, load F1, F2 change according to the axial thickness of internal rotor 2a (be internal rotor 2a along radially the area of pressurized).For example, if internal rotor 2a is thin in the axial direction, load F1, F2 are little, and the moment M1 of the first power reduces.Thus, the moment M2 that be used for to reduce the second power of M1 also can reduce, thus cone angle θ i or the scope of taper is set also can be smaller.In motor part 3 sides, by suppressing the inclination of axle 30, the air gap that can be suppressed between rotor part 3a and stator department 3b produces the situation of axial deflection, thereby motor part 3 is worked swimmingly.At this, as shown in Figure 7, because the axle center of axle 30 is moved to y axle postive direction lateral deviation with respect to the axle center of axle accepting hole 410, if therefore with the axle center of stator department 3b (stator accepting hole 420) with respect to the axle center of axle accepting hole 410 in advance to ejection area side (y axle postive direction side) skew same amount, can suppress air gap and produce radially deflection.That is, make air gap axially and the footpath upwards constant, thereby motor part 3 is worked more swimmingly.Need to prove, external rotor 2b in pump accepting hole 400 with respect to internal rotor 2a aligning automatically.
At this, as utilizing pressure to suppress the method for the inclination of internal rotor 2a, also can taper be set the flank of tooth 21 at internal rotor 2a unlike embodiment 1, and consider for example following situation.That is, at the ejiction opening of second housing 4b side setting with the area opening larger than the ejiction opening 402 of the first shell 4a.Thus, in ejection zone (y axle negative direction side), the load of bearing as internal rotor 2a, the load that the load of being born by the end face with bearing portion 41 opposition sides (x axle postive direction side) is born greater than the end face by bearing portion 41 sides (x axle negative direction side).Thus, therefore the difference of this load reduces the moment M1 of the first power to the effect of x axle negative direction, suppresses the inclination of internal rotor 2a.Yet, in the method, need to newly be provided as in second housing 4b side the ejiction opening of pressure chamber, so structure becomes complicated, and pump may maximize.With respect to this, in embodiment 1, only just can suppress the inclination of internal rotor 2a by at the flank of tooth 21, taper being set, therefore compare with said method, the energy simplified structure, and, easily realize the miniaturization of pump 1.
In addition, the flank of tooth 22 of external rotor 2b has cone angle θ o (with reference to Fig. 3), along with from bearing portion 41 sides (x axle negative direction side) towards with bearing portion 41 opposition sides (x axle postive direction side), and the distance from the axle center of external rotor 2b to the flank of tooth 22 shortens gradually.So, not only the flank of tooth 21 at internal rotor 2a arranges taper, and the flank of tooth 22 at external rotor 2b also is provided with taper for the flank of tooth 21 that suppresses two rotor 2a, 2b, the minimum range (tip clearance) of 22 change on axially (x axle direction).Thus, the situation that the flank of tooth 21 of inhibition internal rotor 2a and the flank of tooth 22 of external rotor 2b interfere, thus can effectively reduce because of the tactile noise (beating dental) that causes of toe joint.And, can reduce the leakage of the oil between adjacent pump chamber r, suppress the decline of pump efficiency.Particularly, at least at the position that the flank of tooth 21 that makes progress in week, the distance of 22 become minimum, with θ o be set as with θ i about equally.Thus, tip clearance axially can remained constant on (x axle direction), thereby can improve above-mentioned action effect.
Taper is made as uniform angle on the whole circumference of two rotor 2a, 2b.Particularly, the flank of tooth 21 of internal rotor 2a has angle θ i on the whole circumference of internal rotor 2a, and θ i is constant on the whole circumference of internal rotor 2a.So, by in (at the bottom of the comprising tooth top and tooth) of the flank of tooth 21 of internal rotor 2a circumferentially whole installation taper, and can enlarge as much as possible the scope that taper is set.Thus, can increase the moment M2 of the second power that produces because of taper, thereby can increase the inclination restraint.And the flank of tooth 22 of external rotor 2b has angle θ o on the whole circumference of external rotor 2b, and θ o is constant on the whole circumference of external rotor 2b.So, by with uniform angle θ i, θ o, taper being set, can easily make two rotor 2a, 2b.
Need to prove, in embodiment 1, making the number of teeth of internal rotor 2a and external rotor 2b poor is 1 and two gear multiple spot Continuous Contact (maintenance tip clearance) and rotation simultaneously, but is not limited to this, and also can make the number of teeth poor is more than 2.In an embodiment, be 1 because the number of teeth is poor, therefore can obtain significantly the inhibition of the noise that the tooth interference each other of two rotor 2a, 2b causes.And, also embodiment 1 cone structure can be applicable to have other the crescent gear pump of profile of tooth such as involute.In embodiment 1, the profile of tooth of two rotor 2a, 2b is the trochoid profile of tooth.Thus, easy processing, and easily make.And, also can utilize internal-combustion engine etc. to drive embodiment 1 crescent gear pump (pump section 2).Embodiment 1 pump 1 is the motor-drive pump that pump section 2 is driven by motor (motor part 3).Thus, by improving the quietness of pump 1, can improve its quality and commodity.And embodiment 1 motor-drive pump 1 is applicable to carry the hydraulic equipment (automatic transmission) on vehicle.Thus, be when carrying out the vehicle of idle stop or electrical motor vehicle etc. at above-mentioned vehicle, by improving the quietness of pump 1, and can improve quality and the commodity of vehicle.For example, in the idle stop car, the motor-drive pump that is applicable to automatic transmission is many to be used under the medium squelch of engine stop, thereby the raising of quietness becomes problem.With respect to this, embodiment 1 pump 1 touches by the toe joint that reduces rotor the noise that causes, and can improve quietness.
[embodiment 1 effect]
Below, enumerate embodiment 1 pump section 2 and the effect that pump 1 plays.
(1) possess: internal rotor 2a, it is fixed on by the bearing that is arranged at shell 4 (bearing portion 41) supporting is on rotation live axle (axle 30) freely, and has external tooth; External rotor 2b, it is arranged in the pump accepting hole 400 that is formed at shell 4 with trip embedding state, have internal tooth and mesh with internal rotor 2a, wherein, at least a portion of the flank of tooth 21 of internal rotor 2a has with respect to the axle of internal rotor 2a than zero the first large angle θ i, and along with from bearing side (x axle negative direction side) towards the distance apart from the axle center of internal rotor 2a shortens gradually with bearing opposition side (x axle postive direction side).
Thus, utilize taper to suppress the inclination of internal rotor 2a, can reduce thus by toe joint and touch the noise (beating dental) that causes.
(1-1) possess: pump structure body (pump section 2), it comprise the internal rotor 2a on an end (x axle postive direction end) that has external tooth and be arranged on axle 30 and have internal tooth and with the external rotor 2b of internal rotor 2a engagement as pump rotor, by making pump rotor 2a, 2b rotation, and the fluid (oil) that will be sucked by sucting (be present in suck zone pump chamber r) is from blowing unit (the pump chamber r that is present in the ejection zone) ejection; Motor (motor part 3), it is arranged on the other end (x axle negative direction end) of axle 30, comes live axle 30 rotations by energising, transmits rotating force via axle 30 to internal rotor 2a; Shell 4, its intermediate portion supporting that is arranged on axle 30 is on rotation bearing (bearing portion 41) freely, and pump structure body and motor are housed in inside.
Thus, utilize taper to suppress the inclination of internal rotor 2a (axle 30), motor part 3 is worked swimmingly, and can improve its quality and commodity by the quietness that improves motor-drive pump 1.
(2) at least a portion of the flank of tooth 22 of external rotor 2b has with respect to the axle of external rotor 2b than zero the second large angle θ o, and along with from bearing side (x axle negative direction side) towards the distance apart from the axle center of external rotor 2b shortens gradually with bearing opposition side (x axle postive direction side).
Thus, suppress tip clearance in axial (x axle direction) upper situation about changing, beat dental thereby can effectively reduce, and, the decline of pump efficiency can be suppressed.
(3) flank of tooth 21 of internal rotor 2a has the first angle θ i on the whole circumference of internal rotor 2a, the first angle θ i is constant on the whole circumference of internal rotor 2a, the flank of tooth 22 of external rotor 2b has described the second angle θ o on the whole circumference of external rotor 2b, the second angle θ o is constant and equate with the first angle θ i on the whole circumference of external rotor 2b.
Thus, can increase taper to the inclination restraint of internal rotor 2a.
[embodiment 2]
In the design of internal rotor 2a, along with from bearing portion 41 sides (x axle negative direction side) towards with bearing portion 41 opposition sides (x axle postive direction side), and the creation circular diameter of internal rotor 2a increases gradually and Base radius reduces gradually.Thus, as shown in Figure 9, the flank of tooth 21 at internal rotor 2a is set as conical in shape, this conical in shape along with from bearing portion 41 sides (x axle negative direction side) towards the distance from the axle center of internal rotor 2a to the flank of tooth 21 shortens gradually with bearing portion 41 opposition sides (x axle postive direction side).In the regulation of tooth top side zone (carrying out the zone of the tooth top side of the timesharing such as 2 at the bottom of to tooth and between tooth top), along with from the tooth bottom side towards the tooth top side and cone angle θ i reduces.Cone angle θ i is to deviate from the degree of (surpass) to the distance of the flank of tooth 21 with respect to reference range (the above-mentioned distance when cone angle θ i is zero) from the axle center of internal rotor 2a relevant.Thus, along with from the tooth bottom side towards the tooth top side and the situation that cone angle θ i reduces represent along with from the tooth bottom side towards the tooth top side and the above-mentioned degree that deviates from reduces.In embodiment 2, at the tooth top (summit) of internal rotor 2a, the above-mentioned degree that deviates from becomes zero, and the flank of tooth 21 is made as zero with respect to the axle angulation (cone angle θ i) of internal rotor 2a.On the other hand, (carry out the zone of the tooth bottom side of the timesharing such as 2 at the bottom of to tooth and between tooth top) in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and cone angle θ i reduces.In embodiment 2, at the bottom of the tooth of internal rotor 2a (summit), the above-mentioned degree that deviates from becomes zero, and cone angle θ i is made as zero.
In the design of external rotor 2b, along with from bearing portion 41 sides (x axle negative direction side) towards with bearing portion 41 opposition sides (x axle postive direction side), and the creation circular diameter of external rotor 2b increases gradually and Base radius reduces gradually.Thus, as shown in figure 10, the flank of tooth 22 at external rotor 2b arranges conical in shape, this conical in shape along with from bearing portion 41 sides (x axle negative direction side) towards with bearing portion 41 opposition sides (x axle postive direction side), and the distance from the axle center of external rotor 2b to the flank of tooth 22 shortens gradually.(carry out the zone of the tooth bottom side of the timesharing such as 2 at the bottom of to tooth and between tooth top) in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and cone angle θ o reduces.Cone angle θ o to from the axle center of external rotor 2b to the distance of the flank of tooth 22 with respect to reference range (the above-mentioned distance when cone angle θ o is zero) deviate from (lower than) degree relevant.Thus, along with from the tooth top side towards the tooth bottom side and the situation that cone angle θ o reduces represent along with from the tooth top side towards the tooth bottom side and the above-mentioned degree that deviates from reduces.In embodiment 2, at the bottom of the tooth of external rotor 2b (summit), the above-mentioned degree that deviates from becomes zero, and the flank of tooth 22 is made as zero with respect to the axle angulation (cone angle θ o) of external rotor 2b.On the other hand, (carry out the zone of the tooth top side of the timesharing such as 2 at the bottom of to tooth and between tooth top) in the regulation of tooth top side zone, along with from the tooth bottom side towards the tooth top side and cone angle θ o reduces.In embodiment 2, at the tooth top (summit) of external rotor 2b, the above-mentioned degree that deviates from becomes zero, and cone angle θ o is made as zero.Other structure is identical with embodiment 1, and therefore description thereof is omitted.
Next, embodiment 2 effect is described.At least a portion of the flank of tooth 21 of internal rotor 2a (zone except at the bottom of tooth top and tooth) has with respect to the axle of internal rotor 2a than zero large angle θ i, and along with shortening gradually apart from the distance in the axle center of internal rotor 2a from x axle negative direction side towards x axle postive direction side.Thus, similarly to Example 1, produce the moment M2 of the second power due to taper, suppress the inclination of internal rotor 2a, touch thereby can reduce by toe joint the noise (beating dental) that causes.And, at least a portion of the flank of tooth 22 of external rotor 2b (zone except at the bottom of tooth top and tooth) has with respect to the axle of external rotor 2b than zero large angle θ o, and along with shortening gradually apart from the distance in the axle center of external rotor 2b from x axle negative direction side towards x axle postive direction side.Thus, similarly to Example 1, can effectively reduce and beat dental in situation of axially (x axle direction) upper variation by suppressing tip clearance, and, the decline of pump efficiency can be suppressed.Particularly, become on minimum position in the flank of tooth 21 that makes progress in week, the distance of 22 at least, θ o be made as with θ i about equally.Thus, tip clearance axially can remained constant on (x axle direction).
In addition, the flank of tooth 21 of internal rotor 2a is made as cone angle θ i in the regulation zone of tooth top side along with reducing towards the tooth top side from the tooth bottom side, and the flank of tooth 22 of external rotor 2b is made as cone angle θ o along with reducing towards the tooth bottom side from the tooth top side in the regulation zone of tooth bottom side.That is, when changing the intrinsic spray volume of pump section 2, the radial dimension of pump section 2 (pump rotors) may increase the amount that cone angle θ i, θ o are set.With respect to this, the zone that reduces by cone angle θ i, θ o (than other zone) are set when comparing with identical intrinsic spray volume, is compared with the embodiment 1 that taper is set equably, can suppress the increase of the radial dimension of pump section 2.That is, can cut down the space of pump section 2 and realize the miniaturization of pump 1, and can improve the layout of pump section 2.Particularly, the cone angle θ i of the tooth top of internal rotor 2a is zero, and the cone angle θ o at the bottom of the tooth of external rotor 2b is zero.That is, at the bottom of the tooth of the tooth top of internal rotor 2a and external rotor 2b respectively with the axle almost parallel of internal rotor 2a and external rotor 2b.Thus, above-mentioned action effect is maximized.
In addition, the flank of tooth 21 of internal rotor 2a is made as cone angle θ i in the regulation zone of tooth bottom side along with reducing towards the tooth bottom side from the tooth top side, and the flank of tooth 22 of external rotor 2b is made as cone angle θ o in the regulation zone of tooth top side along with reducing towards the tooth top side from the tooth bottom side.Thus, with similarly above-mentioned, the zone that reduces by cone angle θ i, θ o (than other zone) are set, and can suppress the increase of the radial dimension of pump section 2, therefore can realize the miniaturization of pump 1 etc.Particularly, the cone angle θ i at the bottom of the tooth of internal rotor 2a is zero, and the cone angle θ o of the tooth top of external rotor 2b is zero.That is, at the bottom of the tooth of internal rotor 2a and the tooth top of external rotor 2b respectively with the axle almost parallel of internal rotor 2a and external rotor 2b.Thus, above-mentioned action effect is maximized.
In embodiment 2, at the bottom of the tooth of two rotor 2a, 2b and the axle almost parallel of tooth top and each rotor 2a, 2b.Thus, even at the flank of tooth 21,22 of two rotor 2a, 2b, cone angle θ i, θ o are set, also can change the intrinsic spray volume of pump ground diameter at the bottom of the tooth top diameter of two rotor 2a, 2b and tooth is formed the size identical with the situation that taper is not set.And, in embodiment 2, by making as the Base radius of the parameter of the profile of tooth of two rotor 2a, 2b and creation circular diameter along axially gradually changing, and realize above-mentioned each structure.Particularly, along with from bearing portion 41 sides (x axle negative direction side) towards with bearing portion 41 opposition sides (x axle postive direction side), the creation circular diameter of internal rotor 2a increases gradually and Base radius reduces gradually, and the creation circular diameter of external rotor 2b increases gradually and Base radius reduces gradually.By simple designs like this, the cone angle θ i of two rotor 2a, 2b, θ o can arrange along with towards tooth top side and tooth bottom side and reduce gradually such conical in shape.
Below, enumerate embodiment 2 pump section 2 and the effect that pump 1 plays.
(4) flank of tooth 21 of internal rotor 2a is in the regulation zone of tooth top side, along with from the tooth bottom side towards the tooth top side and angle θ i reduces, the flank of tooth 22 of external rotor 2b in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and angle θ o reduces.
Thus, can suppress the increase of the radial dimension of pump section 2.
(5) flank of tooth 21 of the tooth top of internal rotor 2a is zero with respect to the axle angulation θ i of internal rotor 2a, and the flank of tooth 22 at the bottom of the tooth of external rotor 2b is zero with respect to the axle angulation θ o of external rotor 2b.
Thus, can make the maximum effect of above-mentioned (4).
(6) flank of tooth 21 of internal rotor 2a is in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and angle θ i reduces, the flank of tooth 22 of external rotor 2b in the regulation zone of tooth top side, along with from the tooth bottom side towards the tooth top side and angle θ o reduces.
Thus, can suppress the increase of the radial dimension of pump section 2.
(7) flank of tooth 21 at the bottom of the tooth of internal rotor 2a is zero with respect to the axle angulation θ i of internal rotor 2a, and the flank of tooth 22 of the tooth top of external rotor 2b is zero with respect to the axle angulation θ o of external rotor 2b.
Thus, can make the maximum effect of above-mentioned (6).
(8) profile of tooth of pump rotor 2a, 2b is the trochoid profile of tooth.
Thus, easy to manufacture.
(9) parameter of the profile of tooth of pump rotor 2a, 2b is Base radius and creation circular diameter axially gradually changing along pump rotor 2a, 2b, along with from bearing side (x axle negative direction side) towards with bearing opposition side (x axle postive direction side), the creation circular diameter of internal rotor 2a increases gradually and Base radius reduces gradually, along with from the bearing side towards with the bearing opposition side, the creation circular diameter of external rotor 2b increases gradually and Base radius reduces gradually.
Thus, by simple design, just can obtain the effect of above-mentioned (4) (6) plyability.
(10) tooth top of pump rotor 2a, 2b and the flank of tooth at the bottom of tooth 21, the 22 axle angulation θ i with respect to pump rotor 2a, 2b, θ o are zero.
Thus, utilize conical in shape to suppress the inclination of internal rotor 2a, and the radial dimension of pump section 2 can be suppressed to the size identical with the situation that taper is not set.
[other embodiment]
Above, although illustrated based on embodiment and be used for realizing mode of the present utility model, concrete structure of the present utility model is not defined as embodiment, and the design alteration etc. of scope that does not break away from the purport of model utility is also contained in the utility model.For example, shell can be made of a plurality of members as embodiment, also can be made of solid memder, can also be divided into a plurality of members different from embodiment.The configuration that sucks oil circuit and ejection oil circuit etc. is not limited to embodiment's situation.And cone angle can be constant at the axial gamut of pump rotor, also can change according to the axial position of pump rotor.In an embodiment, cone angle is arranged on the axial gamut (end face from a side end face to the opposing party) of pump rotor, but also cone angle can be arranged on the scope of axial part.As embodiment when axially gamut arranges cone angle, can increase the inclination restraint of the internal rotor that taper produces.
Claims (10)
1. crescent gear pump is characterized in that possessing:
Internal rotor, it is fixed on by the bearing supporting that is arranged at shell is on rotation live axle freely, and has external tooth;
External rotor, it is arranged in the pump accepting hole that is formed at described shell with trip embedding state, and have internal tooth and mesh with described internal rotor,
At least a portion of the flank of tooth of described internal rotor has with respect to the axle of described internal rotor than zero the first large angle, and along with shortening gradually apart from the distance in the axle center of described internal rotor from described bearing side towards the opposition side of described bearing.
2. crescent gear pump according to claim 1, is characterized in that,
At least a portion of the flank of tooth of described external rotor has with respect to the axle of described external rotor than zero the second large angle, and along with shortening gradually apart from the distance in the axle center of described external rotor from described bearing side towards the opposition side of described bearing.
3. crescent gear pump according to claim 2, is characterized in that,
The flank of tooth of described internal rotor has described the first angle on the whole circumference of described internal rotor, described the first angle is constant on the whole circumference of described internal rotor,
The flank of tooth of described external rotor has described the second angle on the whole circumference of described external rotor, described the second angle is constant and equate with described the first angle on the whole circumference of described external rotor.
4. crescent gear pump according to claim 2, is characterized in that,
The flank of tooth of described internal rotor in the regulation zone of tooth top side, along with from the tooth bottom side towards the tooth top side and described the first angle reduces,
The flank of tooth of described external rotor in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and described the second angle reduces.
5. crescent gear pump according to claim 4, is characterized in that,
The flank of tooth of the tooth top of described internal rotor is zero with respect to the axle angulation of described internal rotor,
The flank of tooth at the bottom of the tooth of described external rotor is zero with respect to the axle angulation of described external rotor.
6. crescent gear pump according to claim 2, is characterized in that,
The flank of tooth of described internal rotor in the regulation zone of tooth bottom side, along with from the tooth top side towards the tooth bottom side and described the first angle reduces,
The flank of tooth of described external rotor in the regulation zone of tooth top side, along with from the tooth bottom side towards the tooth top side and described the second angle reduces.
7. crescent gear pump according to claim 6, is characterized in that,
The flank of tooth at the bottom of the tooth of described internal rotor is zero with respect to the axle angulation of described internal rotor,
The flank of tooth of the tooth top of described external rotor is zero with respect to the axle angulation of described external rotor.
8. crescent gear pump according to claim 1, is characterized in that,
The profile of tooth of described internal rotor and described external rotor is the trochoid profile of tooth.
9. crescent gear pump according to claim 8, is characterized in that,
The parameter of the profile of tooth of described internal rotor and described external rotor be Base radius and creation circular diameter along axially the gradually changing of described internal rotor and described external rotor,
Along with from the opposition side of described bearing side towards described bearing, the creation circular diameter of described internal rotor increases gradually and Base radius reduces gradually,
Along with from the opposition side of described bearing side towards described bearing, the creation circular diameter of described external rotor increases gradually and Base radius reduces gradually.
10. crescent gear pump according to claim 9, is characterized in that,
The tooth top of described internal rotor and the flank of tooth at the bottom of tooth are zero with respect to the axle angulation of described internal rotor,
The tooth top of described external rotor and the flank of tooth at the bottom of tooth are zero with respect to the axle angulation of described external rotor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012067483A JP2013199849A (en) | 2012-03-23 | 2012-03-23 | Internal gear pump |
| JP2012-067483 | 2012-03-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202946371U true CN202946371U (en) | 2013-05-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220434863 Expired - Fee Related CN202946371U (en) | 2012-03-23 | 2012-08-29 | Internal gear pump |
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| Country | Link |
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| JP (1) | JP2013199849A (en) |
| CN (1) | CN202946371U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105229306A (en) * | 2014-03-04 | 2016-01-06 | 日立汽车系统株式会社 | Electric oil pump |
| CN107208628A (en) * | 2015-01-23 | 2017-09-26 | 株式会社电装 | Petrolift and its manufacture method |
| CN108533431A (en) * | 2018-05-29 | 2018-09-14 | 象山申达轿车配件厂 | A kind of engine idling start stop system oil pump |
| US20220356876A1 (en) * | 2021-05-05 | 2022-11-10 | Boundary Lubrication Systems LLC | 3-dimensional pump rotor profile |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000027769A (en) * | 1998-07-08 | 2000-01-25 | Unisia Jecs Corp | Internal gear pump or motor, and manufacture thereof |
| JP4160604B2 (en) * | 2006-04-07 | 2008-10-01 | ジヤトコ株式会社 | Internal gear type oil pump |
| DE102006056845A1 (en) * | 2006-12-01 | 2008-06-05 | Robert Bosch Gmbh | Delivery unit e.g. citation pump of electrical submersible pump systems and an oil pump for internal combustion engine, has gear train, internal gear wheel and external gear wheel |
| JP2010019204A (en) * | 2008-07-14 | 2010-01-28 | Sumitomo Electric Sintered Alloy Ltd | Rotor for internal gear pump |
| DE102010027835A1 (en) * | 2010-04-16 | 2011-10-20 | Robert Bosch Gmbh | gear pump |
-
2012
- 2012-03-23 JP JP2012067483A patent/JP2013199849A/en active Pending
- 2012-08-29 CN CN 201220434863 patent/CN202946371U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105229306A (en) * | 2014-03-04 | 2016-01-06 | 日立汽车系统株式会社 | Electric oil pump |
| CN105229306B (en) * | 2014-03-04 | 2017-10-13 | 日立汽车系统株式会社 | Electric oil pump |
| CN107208628A (en) * | 2015-01-23 | 2017-09-26 | 株式会社电装 | Petrolift and its manufacture method |
| CN108533431A (en) * | 2018-05-29 | 2018-09-14 | 象山申达轿车配件厂 | A kind of engine idling start stop system oil pump |
| US20220356876A1 (en) * | 2021-05-05 | 2022-11-10 | Boundary Lubrication Systems LLC | 3-dimensional pump rotor profile |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013199849A (en) | 2013-10-03 |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130522 Termination date: 20160829 |