CN103727026B - A kind of crescent gear pump - Google Patents
A kind of crescent gear pump Download PDFInfo
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- CN103727026B CN103727026B CN201410038255.7A CN201410038255A CN103727026B CN 103727026 B CN103727026 B CN 103727026B CN 201410038255 A CN201410038255 A CN 201410038255A CN 103727026 B CN103727026 B CN 103727026B
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- 206010020843 Hyperthermia Diseases 0.000 description 1
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Abstract
The invention provides a kind of crescent gear pump, comprise a ring gear pressure equaliser, an axial automatic floating compensation device and two radial automatic floating compensation devices, wherein, ring gear pressure equaliser is formed by establishing reeded outer swing link and ring gear, hydraulic coupling suffered by energy active balance ring gear and gear mesh force, reduce ring gear to the active force of the pump housing, reduction ring gear and the pump housing wear and tear, realize delivery pressure higher time crescent gear pump can normally work for a long time, greatly extend the life-span of gear pump; Axial automatic floating compensation device is made up of left and right thrust plate, left and right inner cover plate etc., radial automatic floating compensation device is made up of oil outlet groove, ring gear and hyperbaric chamber and is made up of inside and outside swing link, spring sheet and Stamping Steel Ribbon etc., three automatic floating compensation devices realize the automatic floating after wearing and tearing between ring gear both ends of the surface gap and ring gear, gear and moon block teeth and compensate, reduce the pressure loss, improve delivery pressure and working efficiency.
Description
Technical field
The present invention relates to gear pump field, especially, relate to a kind of crescent gear pump.
Background technique
The outstanding advantages such as crescent gear pump has compact structure, flow pulsation is little, pressure is large, noise is low, self-priming performance is good, speed range is large, comprise the external gear a pair with involute profile and internal gear engages each other, external gear is driving wheel, internal gear is follower, with moon block teeth, oil sucting cavity and pumping cavity are separated between the two, two gears turn to identical, the gear teeth entering oil sucting cavity exit engagement, thus oil sucting cavity volume is increased, form vacuum, fluid is inhaled under barometric pressure effect, and two gears bring the fluid of oil sucting cavity into pumping cavity; Enter pumping cavity gear and enter engagement, pumping cavity smaller volume, fluid is forced out, and completes oil extraction process.Ring gear due to crescent gear pump is subject to the hydraulic coupling of fluid and making a concerted effort of gear mesh force, annular gear outer-wall produces larger pressure to the pump housing, when ring gear operates under high rotating speed and high oil pressure conditions, annular gear outer-wall is to the contact stress of pump housing inwall and the linear velocity acceptability limit value considerably beyond material, as badly in lubrication effect severe friction will be produced, thus generation adhesive wear, ring gear and the pump housing are produced glue together, crescent gear pump is caused to lose efficacy, therefore, when delivery pressure exceedes certain value, wearing and tearing between the ring gear of crescent gear pump and the pump housing aggravate gradually, the raising of the working pressure of restriction crescent gear pump.
Adopt axial float compensation device and/or radial floating compensation device in prior art or set up composite bush and solve ring gear outer surface and the wear problem of pump housing internal surface when high pressure oil works, but ring gear outer surface contacts between internal surface with the pump housing and wear problem between ring gear, small gear and moon block teeth still exists, cause pressure transient or decline, use inconvenience.
Also the product that can solve the internally engaging pump of above-mentioned wear problem is had at present, but complex structure, manufacturability is poor, and manufacture cost strengthens, and practicability is not strong.
Therefore, design that a kind of structure is simplified, the crescent gear pump of abrasiveness, good stability has very important significance.
Summary of the invention
The object of the invention is to provide a kind of crescent gear pump, effectively can solve the wear problem of ring gear and the pump housing under high workload pressure, ensure that crescent gear pump works long hours under high workload pressure, maintain the feature such as low noise, high efficiency, concrete technological scheme is as follows simultaneously:
A kind of crescent gear pump, comprises housing, gear shaft, ring gear and swing link;
Described housing is the entirety pump housing, left inside cover plate, left outside cover plate, right inside cover plate and right outside cover plate connected by stud bolt;
The internal surface of described left inside cover plate and described right inside cover plate is respectively equipped with composite sliding bearing; Check ring, packing ring and outside framework oil seal is provided with in the endoporus of described right outside cover plate;
The upper end face of the described pump housing is provided with filler opening, and its side is provided with oil outlet, and the surface of internal cavity through with described oil outlet is provided with oil outlet groove;
Described gear shaft is provided with left axle journal, gear and right axle journal, described left axle journal is installed on the internal surface of left thrust plate and composite sliding bearing, and described right axle journal is installed on the internal surface of right thrust plate, composite sliding bearing, spring flange, packing ring and outside framework oil seal and stretches out described right outside cover plate;
Be provided with left fixing ring between described left inside cover plate and described left thrust plate, between described right inside cover plate and right thrust plate, be provided with right fixing ring; Described left thrust plate and described right thrust plate are equipped with oil through, and described right thrust plate is provided with the eyebrow groove be communicated with described oil through;
Described ring gear is arranged on the internal surface of the described pump housing, and is meshed with described gear; The outer annulus edge of described ring gear is evenly equipped with the turnover oilhole at 1-2 row central position and radial offset α angle;
Described swing link comprises interior swing link and outer swing link, and the internal surface of described interior swing link and the cylindrical of described gear fit tightly, and the outer surface of described outer swing link and the inner circle of described ring gear fit tightly; The position radial direction that described outer swing link is meshed with described ring gear is provided with groove.
Preferred in above technological scheme, described interior swing link and outer swing link are all arranged on special-shaped locating stud.
Preferred in above technological scheme, described groove is arranged on the middle part of described outer swing link, and the quantity of described groove is more than or equal to 1.
Preferred in above technological scheme, described groove is triangular groove, and the transverse cross-sectional profile of triangular groove is V-type, and its v-angle is 45 °-75 °, and its length is 5-10mm.
Preferred in above technological scheme, described groove is 2 symmetrically arranged triangular grooves.
Preferred in above technological scheme, described outer swing link is also provided with passage, and two described grooves are symmetricly set on above and below described passage, and the inside of described passage communicates with the inside of described groove; Described in the distance between center line of described passage, the perpendicular distance of the upper-end surface of outer swing link is 15-25mm, is 0-10mm apart from the perpendicular distance of the left and right center line of described outer swing link.
Preferred in above technological scheme, the left surface of described outer swing link and right flank are arranged with opening slot, and the width of described opening slot is 1-5mm, and its degree of depth is 0.5-2.0mm, and described in its center line-spacing, the distance of outer swing link upper-end surface is 15-25mm; Described groove is symmetricly set on the both sides of described outer swing link, and the inside of described groove communicates with the inside of described opening slot respectively.
Preferred in above technological scheme, described groove is triangular groove, and its quantity is more than or equal to 1, and its length is 5-10mm.
Preferred in above technological scheme, described triangular groove is 2, and it is symmetricly set on above and below described opening slot.
Preferred in above technological scheme, described α angle is 10 °-20 °.
The present invention has following beneficial effect:
(1) the position radial direction that the present invention is meshed with ring gear by outer swing link is provided with groove, form ring gear pressure equaliser, can hydraulic coupling suffered by active balance ring gear and gear mesh force, reduce ring gear to the active force of the pump housing, by the setting of outer swing link triangular groove, oil film between available protecting ring gear and the pump housing, reduce the wearing and tearing of ring gear outer surface and pump housing internal surface, realize delivery pressure higher time crescent gear pump can normally work for a long time, greatly extend the life-span of gear pump; Realize the automatic floating after wearing and tearing between ring gear both ends of the surface gap and ring gear, gear and moon block teeth by an axial automatic floating compensation device and two radial automatic floating compensation devices to compensate, reduce the pressure loss, improve delivery pressure and working efficiency.
(2) in the present invention, swing link and outer swing link are all arranged on special-shaped locating stud, easy for installation, and good seal performance.
(3) further groove of the present invention is triangular groove, and the transverse cross-sectional profile of triangular groove is V-type, and its v-angle is 45 °-75 °, its length is 5-10mm, 2 symmetrical triangular grooves are preferably set, well the pressure oil in pressure oscillation district can be transported to transition zone in advance, improve the stability that gear pump runs.
(4) the present invention China and foreign countries swing link is also provided with passage, two described grooves are symmetricly set on above and below described passage, and the inside of described passage communicates with the inside of described groove, described in the distance between center line of passage, the perpendicular distance of the upper-end surface of outer swing link is 15-25mm, be 0-10mm apart from the perpendicular distance of the left and right center line of described outer swing link, easy to process, channels designs can be diversified, and cylindrical or other shapes can be designed to according to actual needs, the pressure oil in pressure oscillation district can be transported to transition zone by the combination design of passage and groove better in advance, transition zone is made to shift to an earlier date build-up pressure, in transition zone, a power is formed to ring gear, making a concerted effort of the hydraulic coupling that rebalancing ring gear was subject to originally and gear mesh force, greatly reduce ring gear to the active force of the pump housing, oil film between available protecting ring gear and the pump housing, guarantee the normal lubrication of ring gear, thus ensure that part normally works in a high voltage state.
(5) the present invention's China and foreign countries' left surface of swing link and right flank are arranged with opening slot, the width of described opening slot is 1-5mm, and its degree of depth is 0.5-2.0mm, and described in its center line-spacing, the distance of outer swing link upper-end surface is 15-25mm; Described groove is symmetricly set on the both sides of described outer swing link, and the inside of described groove communicates with the inside of described opening slot respectively, and preferably, groove is triangular groove, and its quantity is more than or equal to 1, and its length is 5-10mm; Preferably, triangular groove is 2, it is symmetricly set on above and below described opening slot, opening slot design can be diversified, and various shape can be designed to according to actual needs, the pressure oil in pressure oscillation district can be transported to transition zone by the combination design of opening slot and groove better in advance, improves global stability.
(6) in the present invention, the outer annulus edge of ring gear is evenly equipped with the turnover oilhole at 1-2 row central position and radial offset α angle, α angle is 10 ° ~ 20 °, can guarantee that radial turnover oil is not interrupted and have enough flows and turnover oilhole is located on the unidirectional flank of tooth of ring gear.
Except object described above, feature and advantage, the present invention also has other object, feature and advantage.Below with reference to figure, the present invention is further detailed explanation.
Accompanying drawing explanation
The accompanying drawing forming a application's part is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the structural representation of the crescent gear pump of the preferred embodiment of the present invention 1;
Fig. 2 is the B-B direction view of Fig. 1;
Fig. 3 is the schematic diagram of left thrust plate in Fig. 1;
Fig. 4 is the internal structure schematic diagram of Fig. 1;
Fig. 5 is the structural representation of the first outer swing link in Fig. 1;
Fig. 6 is that the B-B of Fig. 5 is to structural representation;
Fig. 7 is the structural representation of the outer swing link of the second in Fig. 1;
Fig. 8 is the D enlarged view of Fig. 7;
Fig. 9 is another structural representation of the outer swing link of the second in Fig. 1;
Figure 10 is the E enlarged view of Fig. 9;
Figure 11 is the pressure-plotting of crescent gear pump;
Figure 12 is the stressed projection chord length schematic diagram of crescent gear pump;
Figure 13 is the stressed schematic diagram in inside of crescent gear pump.
Embodiment
Below in conjunction with accompanying drawing, embodiments of the invention are described in detail, but the multitude of different ways that the present invention can limit according to claim and cover is implemented.
A kind of crescent gear pump, comprise housing, gear shaft 16, ring gear 17 and swing link, described housing is the entirety pump housing 15, left inside cover plate 25, left outside cover plate 26, right inside cover plate 7 and right outside cover plate 1 connected by stud bolt 5, be fixed by hexagon nut 27 and locating stud 6, refer to Fig. 1 and Fig. 2, overall structure is simplified.
The internal surface of described left inside cover plate 25 and described right inside cover plate 7 is respectively equipped with composite sliding bearing 8; Check ring 3, packing ring 4 and outside framework oil seal 2 is provided with in the endoporus of described right outside cover plate 1.
The upper end face of the described pump housing 15 is provided with filler opening 29, and its side is provided with oil outlet 30, and the surface of internal cavity through with described oil outlet 30 is provided with oil outlet groove 31, is convenient to entering and going out of oil.
Described gear shaft 16 is provided with left axle journal, gear 38 and right axle journal, its termination is with keyway 28, described left axle journal is installed on the internal surface of left thrust plate 24 and composite sliding bearing 8, and described right axle journal is installed on the internal surface of right thrust plate 14, composite sliding bearing 8, spring flange 3, packing ring 4 and outside framework oil seal 2 and stretches out described right outside cover plate 1; Be provided with left fixing ring 12 between described left inside cover plate 25 and described left thrust plate 24, between described right inside cover plate 7 and right thrust plate 14, be provided with right fixing ring 11; The many places, inside of described housing are provided with the first seal ring 9, second seal ring 10 and fixing ring 13.
Described ring gear 17 is arranged on the internal surface of the described pump housing 15, and is meshed with described gear 38; The outer annulus edge of described ring gear 17 is evenly equipped with the turnover oilhole 39 at 1-2 row central position and radial offset α angle, α angle is 10 ° ~ 20 °, has enough flows for guaranteeing radial turnover oil not interrupted and passes in and out the unidirectional flank of tooth that oilhole 39 is located at ring gear 17.
Described left thrust plate 24 and described right thrust plate 14 are equipped with oil through 34, described right thrust plate 14 is provided with the eyebrow groove 35 be communicated with described oil through 34, refer to Fig. 3, when the end face of ring gear 17 is through eyebrow groove 35, high pressure oil flows into oil through 34 by eyebrow groove 35, reaches the effect reducing noise.
Described swing link is positioned by swing link locating stud 18, comprise and be supported on interior swing link 19 on special-shaped locating stud 21 and outer swing link 20, under the effect of spring sheet 22 and seal ring 23, the internal surface of described interior swing link 19 and the cylindrical of described gear 38 are fitted tightly, the outer surface of described outer swing link 20 and the inner circle of described ring gear 17 are fitted tightly; The position radial direction that described outer swing link 20 is meshed with described ring gear 17 is provided with groove 202.
The position radial direction that the outer swing link of crescent gear pump of the present invention is meshed with ring gear is provided with groove, form ring gear pressure equaliser, can hydraulic coupling suffered by active balance ring gear and gear mesh force, reduce ring gear to the active force of the pump housing, by the setting of outer swing link triangular groove, oil film between available protecting ring gear and the pump housing, reduce the wearing and tearing of ring gear outer surface and pump housing internal surface, realize delivery pressure higher time crescent gear pump can normally work for a long time, greatly extend the life-span of gear pump; Realize the automatic floating after wearing and tearing between ring gear both ends of the surface gap and ring gear, gear and moon block teeth by an axial automatic floating compensation device and two radial automatic floating compensation devices to compensate, reduce the pressure loss, improve delivery pressure and working efficiency.
The outer swing link of crescent gear pump of the present invention can be varied, refers to following several structure:
The structure of the first outer swing link 20: described groove 202 is arranged on the middle part of described outer swing link 20, described outer swing link 20 is also provided with passage 201, described groove 202 is 2 triangular grooves being symmetricly set on above and below described passage 201, and the inside of described passage 201 communicates with the inside of described groove 202; The quantity of groove 202 can also be designed to the quantity being more than or equal to 1 according to actual needs, and the transverse cross-sectional profile of triangular groove is V-type, and its v-angle A is 45 °-75 °, and its length L is 5-10mm; Described in the distance between center line of described passage 201, the perpendicular distance d1 of the upper-end surface of outer swing link 20 is 15-25mm, is 0-10mm, refers to Fig. 5 and Fig. 6 apart from the perpendicular distance d2 of the left and right center line of described outer swing link 20.
The structure of the outer swing link 20 of the second: the left surface of described outer swing link 20 and right flank are arranged with opening slot 203, the width d3 of described opening slot 203 is 1-5mm, its degree of depth is 0.5-2.0mm, and described in its center line-spacing, the distance d4 of outer swing link 20 upper-end surface is 15-25mm; Described groove 202 is symmetricly set on the both sides of described outer swing link 20, and the inside of described groove 202 communicates with the inside of described opening slot 203 respectively, and described groove 202 is triangular groove, and its quantity is more than or equal to 1, and its length L is 5-10mm; Described triangular groove is 2, and it is symmetricly set on above and below described opening slot 203, and the shape of described triangular groove is varied, can be designed to the triangular groove of angle, the degree of depth and length combination in any, refer to Fig. 7, Fig. 8, Fig. 9 and Figure 10.
Crescent gear pump of the present invention is designed with a ring gear pressure equaliser, an axial automatic floating compensation device and two radial automatic floating compensation devices:
(1) ring gear pressure equaliser is made up of the outer swing link 20 and ring gear 17 being provided with passage 201, detailed process is as follows: refer to Fig. 4, I is low pressure area, II is transition zone, III is pressure oscillation district, IV is zone of high pressure, V is trigonum, low pressure area I is positioned at low-pressure cavity 33, by the passage 201 on outer swing link 20 and groove 202, the pressure oil in pressure oscillation district III is transported to transition zone II in advance, transition zone II is made to shift to an earlier date build-up pressure, in transition zone II, a power is formed to ring gear, making a concerted effort of the hydraulic coupling that rebalancing ring gear was subject to originally and gear mesh force, greatly reduce ring gear to the active force of the pump housing, oil film between available protecting ring gear and the pump housing, guarantee the normal lubrication of ring gear, thus ensure that part normally works in a high voltage state.
(2) axial automatic floating compensation device is by left thrust plate 24, right thrust plate 14, left fixing ring 12, right fixing ring 11, profiled slot on left inside cover plate 25 and the composition of the profiled slot on right inside cover plate 7, specifically be achieved in that when high pressure oil flows into the profiled slot on left inside cover plate 25 and right inside cover plate 7 by the oil through 34 on the left thrust plate 24 of ring gear bi-side and right thrust plate 14, pressure oil acts on left inside cover plate 25 and right inside cover plate 7, the opposite force of pressure oil acts on left thrust plate 24 and right thrust plate 14, left thrust plate 24 and right thrust plate 14 is made to be close to ring gear bi-side all the time.
(3) two radial automatic floating compensation devices are respectively: form a radial automatic floating compensation device by oil outlet groove 31, ring gear 17 and hyperbaric chamber 32, form another radial automatic floating compensation device by interior swing link 19, outer swing link 20, special-shaped locating stud 21, spring sheet 22 and Stamping Steel Ribbon 23.Above-mentioned two radial automatic floatings compensate and are achieved in that one, pressure oil radial direction in hyperbaric chamber 32 acts on gear 38, ring gear 17, interior swing link 19, outer swing link 20 and the pump housing 15 simultaneously, when the projection plane area of oil outlet groove 31 is slightly less than the projection plane area of hyperbaric chamber 32 on the pump housing 15, ring gear 17 is made to be close to the pump housing 15 internal surface all the time; They are two years old; Pressure oil radial direction in hyperbaric chamber 32 acts on gear 38, ring gear 17, interior swing link 19 and outer swing link 20 simultaneously, when to act between interior swing link 19 and outer swing link 20 surperficial for pressure oil, the internal surface of interior swing link 19 is made to be close to the cylindrical of gear 38 all the time, the outer surface of outer swing link 20 is close to the inner circle of ring gear 17 all the time, wherein, hyperbaric chamber 32 is made up of gear 38, ring gear 17, interior swing link 19, outer swing link 20, special-shaped locating stud, left thrust plate 24 and right thrust plate 14.
Hydraulic coupling suffered by ring gear pressure equaliser active balance ring gear and gear mesh force, reduce ring gear to the active force of the pump housing, reduce the wearing and tearing of ring gear outer surface and pump housing internal surface, realize delivery pressure higher time crescent gear pump can normally work for a long time, greatly extend the life-span of gear pump; Realize the automatic floating after wearing and tearing between ring gear both ends of the surface gap and ring gear, gear and moon block teeth by an axial automatic floating compensation device and two radial automatic floating compensation devices to compensate, reduce the pressure loss, improve delivery pressure and working efficiency.
Be analyzed as follows from the loading angle of crescent gear pump:
Its pressure-plotting as shown in figure 11, wherein Q represents equivalent point, O is top circle, II is transition zone, and I is low pressure area, and W is the corresponding chord length (comprising district of equal value) in zone of high pressure, IV is zone of high pressure, for convenience of calculating, be easy to find out stressed rule, approximate hypothesis: 1, transition zone pressure presses the change of straight line rule; 2, low pressure area is set to be stressed as zero.
If transition zone angle is θ
1, zone of high pressure angle is θ
2, in order to use computer graphics to find out stressed rule more easily, transition zone equivalence is become the zone of high pressure of a θ angle, formula is as follows:
1. θ=21.5 ° are tried to achieve, by the chord length L that can obtain corresponding to High Pressure district that maps by formula
1(internal hydraulic pressure masterpiece is corresponding chord length on gear ring), as shown in figure 12, in figure, Q1 is line of contact, and Q2 is the center line engaged completely, L in figure
2for compensating groove acts on corresponding chord length on gear ring, measured by computer drawing: F
in=BL
1p 2.
Formula 2. in: F
infor internal hydraulic pressure power, B is the ring gear facewidth, L
1for chord length corresponding on the effect of internal hydraulic pressure power and gear ring, p is rated pressure (value 25), MPa.
F
flat=B
1l
2p 3.
Formula 3. in: F
flatfor compensating groove place pressure, B
1for balance groove width, L
2chord length corresponding to compensating groove, p is rated pressure (value 25), MPa.
To map for convenience calculating, the concrete numerical value of three power is reduced the straight length (unit: mm) corresponding to 1200 times, according to the composition principle of physics educational level as shown in figure 13, in figure, Q1 is line of contact, Q2 is the center line engaged completely, acts on size and the direction of ring gear three power: (1) gear mesh force F
nthe direction of power is downward along line of contact; (2) internal hydraulic pressure power F
indirection is perpendicular to chord length L
1; (3) compensating groove place pressure F
flatdirection is perpendicular to chord length L
2.
Internal hydraulic pressure power F
inwith compensating groove place pressure F
flatmake a concerted effort for power F
1, gear mesh force F
nwith power F
1make a concerted effort for F, power F be F
n, F
flat, F
infinal to make a concerted effort, direction as shown in figure 13, is 33.3 ° with compensating groove right-hand member end points angle.
The above compensating groove is the ubiquitous parts of hydraulic gear pump, is positioned at gear pump body oil outlet position, L
2the pump housing in length and the gap of ring gear are greater than other positions, for improving the radial force suffered by ring gear that pumping cavity and oil sucting cavity pressure gap cause.
When crescent gear pump works under high pressure conditions (25MP), the power F being acted on pump housing endoporus by ring gear increases, local rapid warm raising is there will be at the point of action of power F, when after high pressure conditions certain time, local temperature reaches transition point, and oil viscosity drops to limiting value, and oil film rigidity starts to be destroyed, direct friction between metal and metal will be caused, crescent gear pump in the short time, can be made to scrap.
The present invention is middle or two side position open walk and grooves by outer swing link cylindrical, outer swing link cylindrical is near ring gear, each tooth cavity is kept to form separate space, form zones of different (transition zone, fluctuation zone, zone of high pressure etc.), outer swing link passage and groove by fluctuation zone and zone of high pressure through, when ring gear rotates an angle, passage and groove and transition zone are connected, pressure oil is incorporated into transition zone fast, under the effect of pressure oil, transition region produces the power that one acts on ring gear, this power constantly changes in the change at groove position along with gear engagement position, the fluid pressure balance produced the on the one hand part ring gear original suffered F that makes a concerted effort, on the other hand this hydraulic coupling swings along with being engaged in zonule of ring gear, thus the suffered position of making a concerted effort F power position of ring gear is constantly changed, oil film is made to produce localized hyperthermia, realize the function of tempered oil film, the wear problem of ring gear and the pump housing under effective solution high workload pressure, ensure that crescent gear pump works long hours under high workload pressure, maintain low noise simultaneously, the features such as high efficiency, practical.
The present invention refers to table 1 with external comparing of crescent gear pump important technological parameters:
Table 1 crescent gear pump of the present invention compares with external product important technological parameters
Through verification experimental verification, take discharge capacity as the crescent gear pump of 50ml be example, when crescent gear pump working speed is 1500r/min, when delivery pressure is 25Mp, liquid temperature 40 DEG C, efficiency is 95%, when test liquid temperature reaches 80 DEG C, still can normally work; When delivery pressure reaches 35Mp, liquid temperature 40 DEG C, efficiency is 93%, when test liquid temperature reaches 80 DEG C, still can keep normal work.
In sum, crescent gear pump of the present invention compared with prior art, have employed three automatic floating compensation devices and a ring gear pressure equaliser simultaneously, effectively can solve the wear problem of ring gear and the pump housing under high workload pressure, ensure that crescent gear pump works long hours under high workload pressure, maintain the feature such as low noise, high efficiency simultaneously, practical.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a crescent gear pump, is characterized in that: comprise housing, gear shaft (16), ring gear (17) and swing link;
Described housing is the entirety pump housing (15), left inside cover plate (25), left outside cover plate (26), right inside cover plate (7) and right outside cover plate (1) connected by stud bolt (5);
The internal surface of described left inside cover plate (25) and described right inside cover plate (7) is respectively equipped with composite sliding bearing (8); Check ring (3), packing ring (4) and outside framework oil seal (2) is provided with in the endoporus of described right outside cover plate (1);
The upper end face of the described pump housing (15) is provided with filler opening (29), and its side is provided with oil outlet (30), and the surface of internal cavity through with described oil outlet (30) is provided with oil outlet groove (31);
Described gear shaft (16) is provided with left axle journal, gear (38) and right axle journal, described left axle journal is installed on the internal surface of left thrust plate (24) and composite sliding bearing (8), and described right axle journal is installed on the internal surface of right thrust plate (14), composite sliding bearing (8), spring flange (3), packing ring (4) and outside framework oil seal (2) and stretches out described right outside cover plate (1);
Be provided with left fixing ring (12) between described left inside cover plate (25) and described left thrust plate (24), between described right inside cover plate (7) and right thrust plate (14), be provided with right fixing ring (11); Described left thrust plate (24) and described right thrust plate (14) are equipped with oil through (34), and described right thrust plate (14) is provided with the eyebrow groove (35) be communicated with described oil through (34);
Described ring gear (17) is arranged on the internal surface of the described pump housing (15), and is meshed with described gear (38); The outer annulus edge of described ring gear (17) is evenly equipped with the turnover oilhole (39) at 1-2 row central position and radial offset α angle;
Described swing link comprises interior swing link (19) and outer swing link (20), the internal surface of described interior swing link (19) and the cylindrical of described gear (38) fit tightly, and the outer surface of described outer swing link (20) and the inner circle of described ring gear (17) fit tightly; The position radial direction that described outer swing link (20) is meshed with described ring gear (17) is provided with groove (202);
Described groove (202) is arranged on the middle part of described outer swing link (20);
Or, the left surface of described outer swing link (20) and right flank are arranged with opening slot (203); Described groove (202) is symmetricly set on the both sides of described outer swing link (20), and the inside of described groove (202) communicates with the inside of described opening slot (203) respectively.
2. crescent gear pump according to claim 1, is characterized in that: described interior swing link (19) and outer swing link (20) are all arranged on special-shaped locating stud.
3. crescent gear pump according to claim 1, is characterized in that: the quantity of described groove (202) is more than or equal to 1.
4. crescent gear pump according to claim 3, it is characterized in that: described groove (202) is triangular groove, the transverse cross-sectional profile of triangular groove is V-type, and its v-angle (A) is 45 °-75 °, and its length (L) is 5-10mm.
5. crescent gear pump according to claim 4, is characterized in that: described groove (202) is 2 symmetrically arranged triangular grooves.
6. crescent gear pump according to claim 5, it is characterized in that: described outer swing link (20) is also provided with passage (201), two described grooves (202) are symmetricly set on above and below described passage (201), and the inside of described passage (201) communicates with the inside of described groove (202); Described in the distance between center line of described passage (201), the perpendicular distance (d1) of the upper-end surface of outer swing link (20) is 15-25mm, is 0-10mm apart from the perpendicular distance (d2) of the left and right center line of described outer swing link (20).
7. crescent gear pump according to claim 1, it is characterized in that: the width (d3) of described opening slot (203) is 1-5mm, its degree of depth is 0.5-2.0mm, and described in its center line-spacing, the distance (d4) of outer swing link (20) upper-end surface is 15-25mm.
8. crescent gear pump according to claim 7, is characterized in that: described groove (202) is triangular groove, and its quantity is more than or equal to 1, and its length (L) is 5-10mm.
9. crescent gear pump according to claim 8, is characterized in that: described triangular groove is 2, and it is symmetricly set on above and below described opening slot (203).
10. crescent gear pump according to claim 1, is characterized in that: described α angle is 10 °-20 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410038255.7A CN103727026B (en) | 2014-01-26 | 2014-01-26 | A kind of crescent gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410038255.7A CN103727026B (en) | 2014-01-26 | 2014-01-26 | A kind of crescent gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103727026A CN103727026A (en) | 2014-04-16 |
| CN103727026B true CN103727026B (en) | 2016-03-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410038255.7A Expired - Fee Related CN103727026B (en) | 2014-01-26 | 2014-01-26 | A kind of crescent gear pump |
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| Country | Link |
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| CN (1) | CN103727026B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108644104B (en) * | 2018-05-17 | 2023-12-08 | 江苏徐工工程机械研究院有限公司 | Valve plate of plunger type fluid machine and plunger type fluid machine |
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| DE102005044576A1 (en) * | 2005-09-17 | 2007-03-22 | Voith Turbo Gmbh & Co. Kg | Internal gear pump |
| CN202284537U (en) * | 2011-11-08 | 2012-06-27 | 重庆液动科技有限公司 | Inner engaged gear pump with radial compensation function |
| CN102635547A (en) * | 2012-04-16 | 2012-08-15 | 山西斯普瑞机械制造有限公司 | Gear pump |
| CN202431515U (en) * | 2011-11-25 | 2012-09-12 | 李小东 | Gap compensation structure for internal gear pump |
| CN202732332U (en) * | 2012-02-29 | 2013-02-13 | 盐城市驰英机械科技有限公司 | Internal engagement gear pump |
| CN102966535A (en) * | 2012-11-01 | 2013-03-13 | 西安交通大学苏州研究院 | Inside engaged gear pump with static pressure supporting device |
| CN203730305U (en) * | 2014-01-26 | 2014-07-23 | 潘光奇 | Internally-engaged gear pump |
-
2014
- 2014-01-26 CN CN201410038255.7A patent/CN103727026B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005044576A1 (en) * | 2005-09-17 | 2007-03-22 | Voith Turbo Gmbh & Co. Kg | Internal gear pump |
| CN202284537U (en) * | 2011-11-08 | 2012-06-27 | 重庆液动科技有限公司 | Inner engaged gear pump with radial compensation function |
| CN202431515U (en) * | 2011-11-25 | 2012-09-12 | 李小东 | Gap compensation structure for internal gear pump |
| CN202732332U (en) * | 2012-02-29 | 2013-02-13 | 盐城市驰英机械科技有限公司 | Internal engagement gear pump |
| CN102635547A (en) * | 2012-04-16 | 2012-08-15 | 山西斯普瑞机械制造有限公司 | Gear pump |
| CN102966535A (en) * | 2012-11-01 | 2013-03-13 | 西安交通大学苏州研究院 | Inside engaged gear pump with static pressure supporting device |
| CN203730305U (en) * | 2014-01-26 | 2014-07-23 | 潘光奇 | Internally-engaged gear pump |
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|---|---|
| CN103727026A (en) | 2014-04-16 |
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