EP0216999A2 - Aussenzahnradpumpe oder -motor asymmetrischer radialschwebender Art - Google Patents

Aussenzahnradpumpe oder -motor asymmetrischer radialschwebender Art Download PDF

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Publication number
EP0216999A2
EP0216999A2 EP86108080A EP86108080A EP0216999A2 EP 0216999 A2 EP0216999 A2 EP 0216999A2 EP 86108080 A EP86108080 A EP 86108080A EP 86108080 A EP86108080 A EP 86108080A EP 0216999 A2 EP0216999 A2 EP 0216999A2
Authority
EP
European Patent Office
Prior art keywords
radial
unit according
gear
asymmetric
axial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP86108080A
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English (en)
French (fr)
Other versions
EP0216999A3 (de
Inventor
Anqiang Cheng
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0216999A2 publication Critical patent/EP0216999A2/de
Publication of EP0216999A3 publication Critical patent/EP0216999A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to an external gear pump or gear motor unit of asymmetric radial floating type, which can be used in a hydraulic system.
  • the external gear pump has been a key element of the hydraulic system for a considerably long time. Its evloution shows that axial floating compensation was realized as early as in 1930's and 1940's while radial compensation still remains a challenge. Although various structures of radial floating type have been developed, no satisfactory radial floating compensation concept is accepted because the existing structures of radial floating compensation are all of symmetric type. The inherent disadvantage of the symmetric structure is that it is difficult to maintain radial balance of the radial floating block and the pump performance is unsatisfactory.
  • Fig. 1 is a schematic diagram of a symmetric radial floating device.
  • Fig. 2 is a schematic diagram of an asymmetric radial floating device comparison-between F ig. 1 and Fig. 2 shows the principle and structural features of the asymmetric radial floating device.
  • the asymmetric radial floating device as the term suggests, has unequal opening angles, i.e. ⁇ 2 ⁇ ⁇ 1 .
  • a and b are a pair of intermeshing gears
  • a is a drive gear
  • b is a driven gear
  • c is a housing
  • d is a radial sealing inserted between the gears and the housing.
  • Fig. 1 (I) shows the instantaneous state of a certain tooth tip (such as of tooth X in the figure) of the driven gear which has just left the end of the sealing arc.
  • FIG. 1(II) shows the instantaneous state of a certain tooth tip (such as of tooth Y in the figure) of the drive gear which has just left the end of the sealing arc. It is known from what is said above that the gear pump bring the oil into the sealing zone, then the oil is squeezed by the tooth to form a high pressure up to the exist pressure of the oil pump. As shown in Fig. 1(I), the tooth tip of tooth X has left the end of the sealing arc of the sealing block and the recess of tooth X is open into zone P where the oil pressure has reached the the output pressure of the oil pump, but tooth Y has not yet left the sealing zone because of the position difference of gear drive.
  • a certain tooth tip such as of tooth Y in the figure
  • nz is the rotational speed of the gear pump, z is the number of gear teeth.
  • the position of the backpressure chamber is constant and the position of the compensating force F 2 generated by the oil pressure within the said chamber is always on the central line g.
  • F 1 and P 2 both act on the radial sealing shoe, they are not on the same straight line and cannot offset each other. This causes unstability and swinging of the symmetric radial floating device, resulting in abnormal wear and low efficiency.
  • the invention proposes an asymmetric radial floating compensation device wherein a pair of intermeshing gears are also mounted in a housing c, a sealing block d is inserted between the gear and the housing.
  • the tooth tips of both drive and driven gears leave the ends of two sealing arcs of the radial sealing block simultaneously. i.e. both teeth leave the sealing zone simultaneously.
  • the change makes the high-pressure zone at the drive gear side always larger than that at the driven gear side, in other words, the radial separating force F 1 is always inclined to the drive gear side. Then, the position of the backpressure chamber is also inclined to the drive gear side, because it depends on the position of the radial separating force F 1 .
  • the invention proposes a circular backpressure chamber sealed by means of a sealing ring h.
  • the eccentricity e between the central line of the backpressure chamber and the symmetric central line g is determined by the position of the radial separating force F 1 .
  • a planar back of the radial sealing shoe should be adopted instead of a curved one. Since the radial separating force F 1 and the radial compensating force F 2 act on the same straight line, they can offset each other. In this way the inherent radial unbalance of the symmetric floating structure is eliminated.
  • Fig. 3 ' is a lateral sectional view.
  • Fig. 4 is a sectional view along line A-A of Fig. 3.
  • the internal hole of the housing 1 is a hole of irregular shape composed of two holes arranged in ⁇ form and an internal plane 2.
  • the housing configuration is of a squarish cylinder. Inside the housing are arranged a pair of intermeshing gears 3 and 4. And an asymetric radial sealing shoe 5 is inserted between the external circular surface of the gear pair and the internal plane 2.
  • the opening angle at the drive gear side is larger than that at the driven gear side.
  • the enveloping angles are equal.
  • the back surface of the radial sealing block 5 is a plane with a circular backpressure slot in it, a sealing 0-ring 6 and a spacer 7 are provided for high pressure sealing.
  • eccentricity e between the central line 8 of the circular backpressure slot and the symmetric central line 9 of the gear pair, the magnitude of eccentricity e depends on the deviation position of the radial separating force from the symmetric central line 9.
  • Shaft 12 is a drive shaft.
  • Fig. 5 is a sectional view along line B-B of Fig. 3. As shown in Fig. 5, the step end face 18 limits the position of the sealing shoe 5 to prevent axial movement of the sealing block.
  • Four sleeves with four bearings on them, the front side plate, the gear side plate and the radial sealing block are all disposed within the hole of irregular shape in the housing 1 to form an integral part.
  • Fig. 6 is a partial sectional view along line C-C of Fig. 4. It illustrates the configuration of the axial backpressure chamber. There is provided an asymmetric ⁇ -form slot at the back of the rear side plate 17.
  • the external cylindric surface of the bearing 13 supporting the side plates and two arcs 20 and 21 of the radial sealing block 5 form an asymmetric A-form axial backpressure chamber, wherein an asymmetric A-form sealing shoe 22 and a spacer 23 (shown in Fig. 4, not in Fig. 6) form an axial floating sealing device.
  • the axial floating sealing devices on the front side plate and the rear side plate are identifical.
  • Fig. 4 It can also be seen from Fig. 4 that among the four sleeves the sleeve 15 mounted on the drive gear shaft near the drive shaft is a longer one, its extending portion determines the position of the front cover 25.
  • the rear pump cover 26 closes the housing.
  • the housing 1, the front cover 25 and the rear cover 26 are fixed by means of bolts 27 to form an integral part.
  • Fig. 7 illustrates the lateral sectional view of the gear motor which can rotate in both forward and backward directions.
  • the housing should be a bidirectional housing 28 having two internal planes 29 and 30, and two radial sealing block 5 should be installed. The rest is identical with what is in the gear pump.
  • the invention enlarges low-pressure zone and reduces high-pressure zone on the basis of asymmetric theory, improves the engineering level of the gear pump or gear motor by means of the asymmetric axial and radial floating compensation device, gives higher volumetric efficiency because of realization of the bidirectional (axial and radial) floating compensation, has higher mechanical efficiency and reduces the noise due to adopting the integral configuration.
  • the stable radial floating device makes radial sealing of the high-pressure zone practicable.
  • the high-pressure zone is reduced, the radial force is reduced, the lifetime of the gear pump or gear motor is prolonged.
  • the gear type hydraulic machinery can be pressurized up to 32lkg/cm 2 level.
  • a series of products can be manufactured with the technique of the invention according to the different flow rate. Also, single-stage pumps, double pumps and triple pumps can be manufactured in accordance with different operating modes. In a word, the invention develops a wider operating area for the pump or gear motor unit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
EP86108080A 1985-09-29 1986-06-13 Aussenzahnradpumpe oder -motor asymmetrischer radialschwebender Art Withdrawn EP0216999A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN85107186A CN85107186B (zh) 1985-09-29 1985-09-29 非对称型径向浮动式齿轮泵、齿轮马达
CN85107186 1985-09-29

Publications (2)

Publication Number Publication Date
EP0216999A2 true EP0216999A2 (de) 1987-04-08
EP0216999A3 EP0216999A3 (de) 1988-07-20

Family

ID=4795505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86108080A Withdrawn EP0216999A3 (de) 1985-09-29 1986-06-13 Aussenzahnradpumpe oder -motor asymmetrischer radialschwebender Art

Country Status (3)

Country Link
EP (1) EP0216999A3 (de)
JP (1) JPS6275086A (de)
CN (1) CN85107186B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114278559A (zh) * 2022-01-10 2022-04-05 淮安市虎力液压机械有限公司 一种具有调节功能提高运行稳定性的液压齿轮泵

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102094856B (zh) * 2011-01-04 2013-11-13 孟庆龙 一种增加压力的液压装置
JP6252802B2 (ja) * 2013-06-13 2017-12-27 株式会社島津製作所 歯車ポンプ又はモータ
IT201700010437A1 (it) * 2017-01-31 2018-07-31 Casappa Spa Macchina volumetrica

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB787162A (en) * 1956-04-13 1957-12-04 New Prod Corp Improvements in or relating to gear pumps
GB1159315A (en) * 1965-10-12 1969-07-23 Otto Eckerle Improvements in and relating to Gear Pumps and Motors
US3838952A (en) * 1972-01-17 1974-10-01 Komatsu Mfg Co Ltd Gear pump and motor having a sealed lock for preventing hydraulic oil from leaking between the ends of the teeth of the gears

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB787162A (en) * 1956-04-13 1957-12-04 New Prod Corp Improvements in or relating to gear pumps
GB1159315A (en) * 1965-10-12 1969-07-23 Otto Eckerle Improvements in and relating to Gear Pumps and Motors
US3838952A (en) * 1972-01-17 1974-10-01 Komatsu Mfg Co Ltd Gear pump and motor having a sealed lock for preventing hydraulic oil from leaking between the ends of the teeth of the gears

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114278559A (zh) * 2022-01-10 2022-04-05 淮安市虎力液压机械有限公司 一种具有调节功能提高运行稳定性的液压齿轮泵
CN114278559B (zh) * 2022-01-10 2022-09-16 淮安市虎力液压机械有限公司 一种具有调节功能提高运行稳定性的液压齿轮泵

Also Published As

Publication number Publication date
CN85107186B (zh) 1988-11-16
JPS6275086A (ja) 1987-04-06
EP0216999A3 (de) 1988-07-20
CN85107186A (zh) 1986-07-16

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