CN102536795A - Cone spring compensation gear pump - Google Patents
Cone spring compensation gear pump Download PDFInfo
- Publication number
- CN102536795A CN102536795A CN2011104625978A CN201110462597A CN102536795A CN 102536795 A CN102536795 A CN 102536795A CN 2011104625978 A CN2011104625978 A CN 2011104625978A CN 201110462597 A CN201110462597 A CN 201110462597A CN 102536795 A CN102536795 A CN 102536795A
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- gear
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- outer end
- spring
- end cap
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Abstract
The invention relates to a cone spring compensation gear pump, which comprises a driving shaft, a driven shaft, a main gear, a sub gear, a cone main spring, a cone sub spring, an end surface compensation disc, a front outer end cover, an end cover screw, a pump body and a back outer end cover, wherein the end surface compensation disc is arranged among the main gear, the sub gear and the front outer end cover, in addition, the large end of the cone main spring is fixedly arranged at the back concave main ring corner part of the compensation disc, the small end of the cone main spring is pressed and leaned on the inner side surface of the front end outer cover, the large end of the cone sub spring is fixedly arranged at the back concave sub ring corner part of the compensation disc, and the small end of the cone sub spring is pressed and leaned at the inner side surface of the front end outer cover. Through the axial rebounding force simultaneously generated by respectively pressing the small end of the cone main spring and the small end of the cone sub spring on the inner side surface of the front end outer cover, the front plane of the end cover compensation disc is tightly pasted with one side end plane of the main gear and the sub gear, the other side end planes of the main gear and the sub gear are tightly pasted with the inner plane of the back outer end cover, and the gear pump is ensured to be always in high-efficiency operation.
Description
Technical field
The invention belongs to mechanical engineering field, International Classification of Patents is the F04D non-varactor pump, relate to a kind of with mechanical energy convert into fluid pressure can the transformation of energy rotary volume pump, be meant a kind of volute spring compensation gear pump especially.
Background technique
Rotary volume pump has the high advantage of efficient, but all exists its efficient of long-time running wearing and tearing back obviously to reduce, and causes the main cause of above-mentioned defective to be that movable isolation of end face between hyperbaric chamber and the low pressure chamber fail to play effective sealing.The undersized easy heat expansion of end face fit tolerance is stuck firmly; The end face fit tolerance is oversize then fails to play effective sealing; And long-time running wearing and tearing back sealing effect is poorer, and the production line of having to stop is changed pumping unit, causes very big direct waste and indirect loss.
In all rotary volume pumps, vane pump is widely used in each industry and commerce field because of plurality of advantages such as its compact structures.Perplexing its problem that always can not get effectively solving is: behind the long-term high speed operation, must wearing and tearing of its end face can not get effective compensation.China's license notification number: CN1059019C pendulum rotary vane pump; China's license notification number: CN100374725C rotating vane pump; China's license notification number: the arc toothed mesohigh gear pump of CN1316162C asymmetric double; The internal gear pump of China's license notification number: CN1081750C band plastic shell; China's license notification number: CN101120175B and China's license notification number: a CN101403382B gear pump for micro-miniature turbojet engine etc.; All do not see method and measure that practicable effective compensation is arranged, solve the end wear gap control problem of rotary volume pump.
Summary of the invention
The purpose of this invention is to provide a kind of volute spring compensation gear pump; When effectively controlling radial clearance; Also possess end wear compensation isolation technology,, remedy the deficiency of existing technology to realize being in efficient external series gap state of a control all the time between hyperbaric chamber and the low pressure chamber; Fill up rotary volume pump when effectively controlling radial clearance, also possess the technological gap of end wear compensate for clearance control.
To achieve these goals; The present invention provides following technological scheme: a kind of volute spring compensation gear pump; Comprise driving shaft, driven shaft, master gear, from gear, taper main spring, taper from spring, end-face compensate dish, preceding outer end cap, bolts, the pump housing, back outer end cap; The both ends of the surface of the described pump housing are vertical each other with two semicircle orifices, and outer end cap all has bolts fastening with the back outer end cap before being stamped respectively on the both ends of the surface; The protecgulum of outer end cap active axis hole is on the same axis with the bonnet active axis hole of back outer end cap before described; The driven axis hole of protecgulum of outer end cap is on the same axis with the driven axis hole of bonnet of back outer end cap before described, described driving shaft and protecgulum initiatively between axis hole and the bonnet active axis hole for being slidingly matched; Between driven axis hole of described driven shaft and protecgulum and the driven axis hole of bonnet for being slidingly matched, described master gear and driving shaft secure fit and between preceding outer end cap and back outer end cap; Described from gear and driven shaft secure fit and between preceding outer end cap and back outer end cap; Described master gear be meshing with each other from gear; As improvement: described master gear and between gear and preceding outer end cap, the end-face compensate dish is arranged; And compensating disc is carried on the back the big end that the taper main spring is being fixed at place, recessed main ring angle, and the small end of taper main spring is pressed against the inboard face of front end enclosing cover; The compensating disc back of the body is recessed is fixing the big end of taper from spring from the ring angle, and taper is pressed against the inboard face of front end enclosing cover from the small end of spring.
As further improvement: described end-face compensate dish have compensating disc initiatively axis hole and protecgulum initiatively axis hole and bonnet active axis hole are on the same axis; Described end-face compensate dish has driven axis hole of compensating disc and the driven axis hole of protecgulum and the driven axis hole of bonnet to be on the same axis; The two semicircle external frames of the compensating disc of described end-face compensate dish are slidingly matched with two semicircle orifices; The described end-face compensate dish back side also has compensating disc to carry on the back recessed main ring angle and the compensating disc back of the body is recessed from the ring angle.
Structural principle:
External force is through main shaft keyway input, by the related master gear rotation of driving shaft, through master gear be meshing with each other from gear, order about from the gear opposite spin master gear cylindrical and all be slidingly matched with two semicircle orifices from top circle.
Master gear and equal from the gear width.Compensating disc is carried on the back the big end that the taper main spring is being fixed at place, recessed main ring angle, and the small end of taper main spring is pressed against the inboard face of front end enclosing cover; The compensating disc back of the body is recessed is fixing the big end of taper from spring from the ring angle, and taper is pressed against the inboard face of front end enclosing cover from the small end of spring.The common axial rebounding force that produces of inboard face that is pressed against the front end enclosing cover respectively from the small end of spring by means of the small end and the taper of taper main spring; Make the horizontal frontal plane of end-face compensate dish be close to master gear and from a side plane of gear; Force master gear and be close to the inner plane of outer end cap afterwards from the opposite side Transverse plane of gear; Guarantee that gear pump is in high-efficiency operation all the time, constitute axial end wear compensation gap control technology.
Master gear and from gear when rotated through adjacent two tooth working spaces, constantly bring liquid working media into adjacent two tooth working spaces from suction port, after the rotation semi-circumference, squeeze exhaust port, go round and begin again.
The invention has the beneficial effects as follows: the common axial rebounding force that produces of inboard face that is pressed against the front end enclosing cover respectively from the small end of spring by means of the small end and the taper of taper main spring; Make the horizontal frontal plane of end-face compensate dish be close to master gear and from a side plane of gear; Force master gear and be close to the inner plane of outer end cap afterwards, guarantee that gear pump is in high-efficiency operation all the time, constitute axial end wear compensation gap control technology from the opposite side Transverse plane of gear; Novel; Simple in structure, the convenient manufacturing, application market has a high potential.
Description of drawings
Fig. 1 is the whole sectional drawing through two main axiss of the present invention;
Fig. 2 is the P-P sectional view among Fig. 1;
Fig. 3 is the back side stereogram of the end-face compensate dish 40 among Fig. 1;
Fig. 4 is the sectional view in Q-Q cross section among Fig. 1;
Fig. 5 is a R-R step sectional view among Fig. 4.
Embodiment
In conjunction with accompanying drawing and embodiment, further structure of the present invention and working principle are elaborated.
A kind of volute spring compensation gear pump; Comprise driving shaft 11, driven shaft 12, master gear 51, from gear 52, taper main spring 31, taper from spring 32, end-face compensate dish 40, preceding outer end cap 60, bolts 70, the pump housing 80, back outer end cap 90; The both ends of the surface of the described pump housing 80 are vertical each other with pair semicircle orifice 85, and outer end cap 60 all has bolts 70 fastening with back outer end cap 90 before being stamped respectively on the both ends of the surface; The protecgulum of outer end cap 60 active axis hole 61 is on the same axis with the bonnet active axis hole 91 of back outer end cap 90 before described; The driven axis hole 62 of the protecgulum of outer end cap 60 is on the same axis with the driven axis hole 92 of bonnet of back outer end cap 90 before described, described driving shaft 11 and protecgulum initiatively between axis hole 61 and the bonnet active axis hole 91 for being slidingly matched; Between driven axis hole 62 of described driven shaft 12 and protecgulum and the driven axis hole 92 of bonnet for being slidingly matched, described master gear 51 and driving shaft 11 secure fit and between preceding outer end cap 60 and back outer end cap 90; Described from gear 52 and driven shaft 12 secure fit and between preceding outer end cap 60 and back outer end cap 90; Described master gear 51 be meshing with each other from gear 52; As improvement: described master gear 51 and between gear 52 and preceding outer end cap 60, end-face compensate dish 40 is arranged; And compensating disc is carried on the back the big end that taper main spring 31 is being fixed at 431 places, recessed main ring angle, and the small end of taper main spring 31 is pressed against the inboard face of front end enclosing cover 60; The compensating disc back of the body is recessed is fixing the big end of taper from spring 32 from ring angle 432, and taper is pressed against the inboard face of front end enclosing cover 60 from the small end of spring 32.
As further improvement: described end-face compensate dish 40 have compensating disc initiatively axis hole 411 and protecgulum initiatively axis hole 61 and bonnet initiatively axis hole 91 be on the same axis; Described end-face compensate dish 40 has the driven axis hole 412 of compensating disc to be on the same axis with driven axis hole 62 of protecgulum and the driven axis hole 92 of bonnet; The two semicircle external frames 48 of the compensating disc of described end-face compensate dish 40 are slidingly matched with two semicircle orifices 85; Described end-face compensate dish 40 back sides also have compensating disc to carry on the back recessed main ring angle 431 and the compensating disc back of the body is recessed from ring angle 432.
Embodiment's installation steps and working procedure are following.
Installation steps:
In Fig. 1, it is 17 numbers of teeth that embodiment selects master gear 51, also is 17 numbers of teeth from gear 52, and bolts 70 numbers of each side of the pump housing 80 are 6.
On a side end face of the pump housing 80, place gasket seal, rear end enclosing cover 90 is fixed on the side end face of the pump housing 80 with 6 bolts 70.
In the groove of bonnet active axis hole 91, put into driving shaft seal ring 21; In the groove of the driven axis hole 92 of bonnet, put into driven shaft seal ring 22.
With the appropriate location of master gear 51 stationary at driving shaft 11; Will be from the appropriate location of gear 52 stationary at driven shaft 12.Short exposed junction with driving shaft 11 inserts in the bonnet active axis hole 91 again; The short exposed junction of driven shaft 12 inserts in the driven axis hole 92 of bonnet, master gear 51 be meshing with each other from gear 52, make master gear 51 and pasting the inner plane of back outer end cap 90 from a side end face of gear 52.
With the horizontal frontal plane of end-face compensate dish 40 towards master gear 51 with from gear 52; Let compensating disc active axis hole 411 be inserted in the long exposed junction of driving shaft 11; Let the driven axis hole 412 of compensating disc be inserted in the long exposed junction of driven shaft 12; Make master gear 51 and pasting the horizontal frontal plane of end-face compensate dish 40 from the opposite side end face of gear 52, the two semicircle external frames of compensating disc are slidingly matched with two semicircle orifices 85.
The big end of taper main spring 31 is fixed on compensating disc carries on the back 431 places, recessed main ring angle; It is recessed from ring angle 432 again taper to be fixed on the compensating disc back of the body from the big end of spring 32.
In the groove of protecgulum active axis hole 61 and in the groove of the driven axis hole 62 of protecgulum, put into driving shaft seal ring 21 and driven shaft seal ring 22 respectively.
On the opposite side end face of the pump housing 80, place gasket seal; Preceding outer end cap 60 is fixed on the opposite side end face of the pump housing 80 with 6 bolts 70; Make the long exposed junction of driving shaft 11 pass through initiatively axis hole 61 of protecgulum, driving shaft keyway 17 is in outside the preceding outer end cap 60; The long exposed junction of driven shaft 12 passed through the driven axis hole 62 of protecgulum.
During the work operation:
In Fig. 2, external force,, is ordered about from gear 52 opposite spins through master and slave gear engagement by driving shaft 11 related master gears 51 rotations through driving shaft keyway 17 input, master gear 51 cylindricals and all be slidingly matched with two semicircle orifices from gear 52 cylindricals.
Compensating disc is carried on the back the big end that taper main spring 31 is being fixed at 431 places, recessed main ring angle, and the small end of taper main spring 31 is pressed against the inboard face of front end enclosing cover 60; The compensating disc back of the body is recessed is fixing the big end of taper from spring 32 from ring angle 432, and taper is pressed against the inboard face of front end enclosing cover 60 from the small end of spring 32.The common axial rebounding force that produces of inboard face that is pressed against front end enclosing cover 60 respectively from the small end of spring 32 by means of the small end and the taper of taper main spring 31; Make the horizontal frontal plane of end-face compensate dish 40 be close to master gear 51 and from a side plane of gear 52; Force master gear 51 and be close to the inner plane of outer end cap 90 afterwards from the opposite side Transverse plane of gear 52; Constitute axial end wear compensation gap control technology, guarantee that gear pump is in high-efficiency operation all the time.
Claims (2)
1. a volute spring compensates gear pump; Comprise driving shaft (11), driven shaft (12), master gear (51), from gear (52), taper main spring (31), taper from spring (32), end-face compensate dish (40), preceding outer end cap (60), bolts (70), the pump housing (80), back outer end cap (90); The both ends of the surface of the described pump housing (80) are vertical each other with two semicircle orifices (85), be stamped respectively on the both ends of the surface preceding outer end cap (60) and afterwards outer end cap (90) all have bolts (70) fastening; The protecgulum of outer end cap (60) active axis hole (61) is on the same axis with the bonnet active axis hole (91) of back outer end cap (90) before described; The driven axis hole of protecgulum (62) of outer end cap (60) is on the same axis with the driven axis hole of bonnet (92) of back outer end cap (90) before described, described driving shaft (11) and protecgulum initiatively between axis hole (61) and the bonnet active axis hole (91) for being slidingly matched; Between described driven shaft (12) and the driven axis hole of protecgulum (62) and the driven axis hole of bonnet (92) for being slidingly matched, described master gear (51) and driving shaft (11) secure fit and be positioned at preceding outer end cap (60) and back outer end cap (90) between; Described from gear (52) and driven shaft (12) secure fit and be positioned at preceding outer end cap (60) and back outer end cap (90) between; Described master gear (51) be meshing with each other from gear (52); It is characterized in that: described master gear (51) and between gear (52) and preceding outer end cap (60), end-face compensate dish (40) is arranged; And compensating disc is carried on the back the big end that taper main spring (31) is located fixing in recessed main ring angle (431), and the small end of taper main spring (31) is pressed against the inboard face of front end enclosing cover (60); The compensating disc back of the body is recessed is fixing the big end of taper from spring (32) from ring angle (432), and taper is pressed against the inboard face of front end enclosing cover (60) from the small end of spring (32).
2. a kind of volute spring compensation gear pump according to claim 1 is characterized in that: described end-face compensate dish (40) has compensating disc active axis hole (411) and protecgulum active axis hole (61) and bonnet active axis hole (91) to be on the same axis; Described end-face compensate dish (40) has the driven axis hole of compensating disc (412) and driven axis hole of protecgulum (62) and the driven axis hole of bonnet (92) to be on the same axis; The two semicircle external frames (48) of the compensating disc of described end-face compensate dish (40) are slidingly matched with two semicircle orifices (85); Described end-face compensate dish (40) back side also has compensating disc to carry on the back recessed main ring angle (431) and the compensating disc back of the body is recessed from ring angle (432).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011104625978A CN102536795A (en) | 2011-12-27 | 2011-12-27 | Cone spring compensation gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011104625978A CN102536795A (en) | 2011-12-27 | 2011-12-27 | Cone spring compensation gear pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102536795A true CN102536795A (en) | 2012-07-04 |
Family
ID=46344546
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011104625978A Pending CN102536795A (en) | 2011-12-27 | 2011-12-27 | Cone spring compensation gear pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102536795A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102878071A (en) * | 2012-10-04 | 2013-01-16 | 张意立 | Special gear pump |
| CN102926997A (en) * | 2012-10-28 | 2013-02-13 | 张意立 | Flange internal thread conical spring gear pump |
| CN102927003A (en) * | 2012-12-06 | 2013-02-13 | 张意立 | Special gear pump |
| CN103133342A (en) * | 2013-03-20 | 2013-06-05 | 张意立 | Gear pump with novel structure |
| CN105840499A (en) * | 2015-02-03 | 2016-08-10 | 曼卡车和巴士股份公司 | Method for Operating a Gear Pump, and Gear Pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0893655A (en) * | 1994-09-27 | 1996-04-09 | Shimadzu Corp | Gear pump or motor |
| JPH10141245A (en) * | 1996-11-01 | 1998-05-26 | Koyo Seiko Co Ltd | Gear pump |
| CN201714657U (en) * | 2010-07-02 | 2011-01-19 | 辽宁光大机械制造有限公司 | High pressure gear pump for floating compensation of radical clearance |
| CN102182673A (en) * | 2011-05-18 | 2011-09-14 | 张意立 | Four-line synchromesh spring compensation combination pump |
| CN102182674A (en) * | 2011-05-18 | 2011-09-14 | 张意立 | Five-wire synchronous meshing spring compensation combined pump |
| CN202370839U (en) * | 2011-12-23 | 2012-08-08 | 张意立 | Gear pump compensated by conical spring |
-
2011
- 2011-12-27 CN CN2011104625978A patent/CN102536795A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0893655A (en) * | 1994-09-27 | 1996-04-09 | Shimadzu Corp | Gear pump or motor |
| JPH10141245A (en) * | 1996-11-01 | 1998-05-26 | Koyo Seiko Co Ltd | Gear pump |
| CN201714657U (en) * | 2010-07-02 | 2011-01-19 | 辽宁光大机械制造有限公司 | High pressure gear pump for floating compensation of radical clearance |
| CN102182673A (en) * | 2011-05-18 | 2011-09-14 | 张意立 | Four-line synchromesh spring compensation combination pump |
| CN102182674A (en) * | 2011-05-18 | 2011-09-14 | 张意立 | Five-wire synchronous meshing spring compensation combined pump |
| CN202370839U (en) * | 2011-12-23 | 2012-08-08 | 张意立 | Gear pump compensated by conical spring |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102878071A (en) * | 2012-10-04 | 2013-01-16 | 张意立 | Special gear pump |
| CN102926997A (en) * | 2012-10-28 | 2013-02-13 | 张意立 | Flange internal thread conical spring gear pump |
| CN102926997B (en) * | 2012-10-28 | 2016-03-16 | 张意立 | A kind of flange internal thread volute spring gear pump |
| CN102927003A (en) * | 2012-12-06 | 2013-02-13 | 张意立 | Special gear pump |
| CN102927003B (en) * | 2012-12-06 | 2014-12-24 | 温州市张衡科技服务有限公司 | Special gear pump |
| CN103133342A (en) * | 2013-03-20 | 2013-06-05 | 张意立 | Gear pump with novel structure |
| CN105840499A (en) * | 2015-02-03 | 2016-08-10 | 曼卡车和巴士股份公司 | Method for Operating a Gear Pump, and Gear Pump |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
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| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20120704 |