CN102362073A

CN102362073A - Hydraulic toothed wheel machine

Info

Publication number: CN102362073A
Application number: CN2010800113207A
Authority: CN
Inventors: M.拉策尔; M.威廉; D.施武乔; G.布雷登费尔德; S.塞尔尼; S.特茨拉夫; K.格里泽
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2009-03-12
Filing date: 2010-02-25
Publication date: 2012-02-22
Also published as: WO2010102723A3; JP2012519799A; JP5502909B2; US20120156080A1; WO2010102723A2; EP2406496A2; DE102009012916A1; BRPI1011690A2

Abstract

The invention relates to a toothed wheel machine comprising a housing for receiving two meshing toothed wheels. Said toothed wheels are axially mounted in a sliding manner by axial surfaces between bearing bodies received in the housing, and radially by a bearing shaft received in the bearing bodies. Hydraulic and mechanical forces are generated during the operation of the toothed wheel machine, an axial force component of said forces acting on each toothed wheel in the same axial direction. In order to counteract said axial force component, a pressure field is provided between at least one axial surface of one of the toothed wheels in the direction of action of the axial force component, and the bearing body adjacent to the at least one axial surface.

Description

Hydraulic type gear machine

Technical field

The present invention relates to a kind of by claim 1 hydraulic type gear as described in the preamble machine.

Background technique

A kind of gear machine that has housing has been shown in EP 1 291 526 A2, and two are engaged with each other and are bearing in arrangement of gears in axle sleeve or the bearing support in this housing, and wherein, this housing seals with first and second caps respectively distolateral.Gear axially is being used in each two axial vane surface between the bearing support and supported slidably through the supporting axle that is contained in the bearing support respectively radially.During the operation of gear machine, hydraulic coupling affacts on the gear along the identical gear longitudinal axis respectively with mechanical force.In order to make clutch shaft bearing body on the action direction that is in these power is not that axial vane surface through gear is pressed between the gear and first cap and very little glade plane space between the gear and second bearing support, only occurs, and reaction force is applied on gear and the clutch shaft bearing body.At this, this reaction force is greater than hydraulic coupling and mechanical force, so the clutch shaft bearing body is compressed against on the gear, and gear is compressed against on second bearing support and second bearing support is compressed against on second cap.Make a concerted effort all along the second cap directive effect on bearing support and gear.

Piston through acting on the supporting axle is applied to reaction force on the gear.Piston this by roughly and the gear longitudinal axis coaxially be slidingly received in the dividing plate that is between first cap and the housing; And abut in the first piston end face on the axial end of the sensing first cap direction of supporting axle, and use pressure-loaded respectively through second piston end surface.Reaction force is applied on the clutch shaft bearing body through the pressure field that is formed between bearing support and the dividing plate.

The defective of this solution is that the whole package that is made up of bearing support and gear is pressed against on second cap of gear machine, and therefore second cap and housing receive high and uneven load.Because gear and bearing support are pressed into together, between the axial vane surface of gear and bearing support quite high wearing and tearing have appearred.In addition, reaction force is applied on supporting axle and the bearing support, need because of a plurality of members on equipment and technology than high cost.

Summary of the invention

Technical problem to be solved by this invention is, creates a kind of hydraulic type gear machine, and it is fairly simple on equipment and technology, with a small amount of member structure and have lower wearing and tearing.

This technical problem solves through the described hydraulic type gear of the characteristic machine by claim 1.

According to the present invention, the gear facility have the housing that holds two gears that are engaged with each other.These two gears utilize between the bearing support of axial vane surface in being contained in housing supported slidably and supported slidably with the supporting axle that is contained in the bearing support respectively diametrically in the axial direction.Gear machine when operation, affact on each gear by the identical axial direction of axial thrust load court of the synthetic power of the hydraulic coupling and the mechanical force of emerged in operation.Be at least one of gear on the action direction of axial thrust load axial vane surface and and the bearing support of said at least one axial vane surface adjacency between be provided with at least one pressure field.

The advantage of this solution is, can need not additional member through pressure field and just can a reaction force with the axial thrust load acting in opposition be applied on the gear.Therefore in addition, the axial thrust load as the pressing force effect of gear diminishes through this pressure field, at gear be in sliding friction between the bearing support on the axial thrust load action direction and diminish and wear and tear and be minimized.

Gear is preferably made tooth with being tilted.

In a kind of preferred form of implementation, between slip surface axial vane surface on the action direction that is in axial thrust load of gear and bearing support and that this axial vane surface is opposed, establish a pressure field respectively.The benefit of doing like this is that these pressure fields can have different sizes, therefore can use each gear of different pressure-loaded.

Pressure field can be designed to press the chamber simply.

Advantageously, press the chamber as being inserted in the slip surface that is in the bearing support on the axial thrust load action direction at pressure tank cheap for manufacturing cost.

The preferred concentric ring of first pressure tank is presented in the slip surface of the bearing support on the action direction that is in axial thrust load and second pressure tank is presented in the slip surface of the bearing support on the action direction that is in axial thrust load with the mode around the second bearing hole covering part cyclotomy around the clutch shaft bearing hole, has therefore realized the different acting surface of pressure tank.

Advantageously, pressure tank is connected with the high-pressure medium of gear machine via interface slot.The pressure that affacts in the pressure tank and the operating conditions of gear machine are combined.

In the preferred form of implementation of another kind, press the chamber to be presented to being in the axial vane surface on the axial thrust load action direction of gear.

Press the chamber to be constructed to and to make simply along the circumferential sectors of each supporting axle that centers on gear, very little leakage slit therefore also occurred.

Because can realize uniform pressure-loaded, so advantageously, press the chamber to be configured to each supporting axle around gear to gear.

Preferably press chamber to widen at least one in order to improve the acting surface of pressing the chamber, the amplitude of widening is the teeth groove portion section that is presented in the increment face of tooth of gear.

Press the pressure oil supply in chamber to accomplish, wherein, press the chamber for example to be connected with the high-pressure medium of gear machine through the bearing support of adjacency.

Other favourable expansion design of the present invention is the theme of other dependent claims.

Description of drawings

Next set forth a plurality of embodiments of the present invention in detail by schematic figures.In the accompanying drawing:

Fig. 1 simplifies the gear machine that shows with sectional arrangement drawing;

Fig. 2 simplifies with side view and shows the package that the gear by the gear machine of bearing support and Fig. 1 constitutes;

Fig. 3 shows bearing support and the gear by first kind of embodiment's gear machine with the sectional arrangement drawing simplification;

Fig. 4 is the plan view of the bearing support of Fig. 3; And

Fig. 5 is the plan view by the gear of second kind of embodiment's gear machine.

Embodiment

Show the hydraulic type working machine that is designed to gear machine 1 with the longitudinal section among Fig. 1 by first kind of embodiment.The gear facility have the machine case 2 by two

caps

4 and 6 sealings.Gear machine 1 is passed by first supporting axle 8 at the cap 6 on Fig. 1 the right, and first gear 10 is arranged in machine case 2 on this first supporting axle.First gear 10 is via

helical teeth

14 and 12 engagements of second gear, and wherein, gear 12 is arranged on second supporting axle 16 antitorquely.First and second supporting

axles

8 and 16 guiding in two sliding

bearings

18,20 or 22,24 respectively.Sliding bearing 20,24 on Fig. 1 the right is undertaken in the bearing support 26 at this, and 18,22 on sliding bearing on Fig. 1 left side is undertaken in the bearing support 28.

Gear

10 and 10 is bearing on second bearing support 26 on Fig. 1 the right slidably via first

axial vane surface

30 or 32 respectively and is bearing in slidably on the bearing support 28 on the left side via second

axial vane surface

34 or 36 respectively along axis.Can be equipped with sliding coating at

gear

10,12 and bearing support 26, slip surface between 28, like MoS2, graphite or PTFE (teflon), to reduce

friction.Bearing support

26 and 28 points to

cap

6 or 4 with

end face

38 or 40 respectively.

Cap

4,6 is directed on machine case 2 via centring pin 42.

Cap

4 and 6 and machine case 2 between be furnished with housing seal part 44.In addition, axial field Sealing 46 is presented to respectively in the

end face

38 and 40 of

bearing support

26 or 28, so that the high-pressure area and the area of low pressure of gear machine 1 separated.The perforation of the cap 6 that passes Fig. 1 the right of another Simmer ring 48 sealings first supporting axle 8.

When 1 operation of gear machine, hydraulic coupling and mechanical force occur, this is explained in detail in ensuing Fig. 2 schematically.

Fig. 2 simplifies with side view and shows by

gear

10 and 12 and the package that constitutes of

bearing support

26 and 28, so as the hydraulic coupling that occurs when being illustrated in gear machine 1 operation of Fig. 1 with mainly pass through the mechanical force that helical teeth 14 acts on.The component of hydraulic coupling in two

gears

10,12 towards identical axial action (among Fig. 2 left).Additionally; A mechanical component of mechanical force affacts on the actuation gear along the action direction of hydraulic pressure component; That is on the upper gear in Fig. 2 10, mechanical component then affacts on the driven gear with the action direction of hydraulic pressure component on the contrary, that is on the undergear among Fig. 2 12.Hydraulic pressure component and mechanical component produce one respectively along equidirectional (being left among Fig. 2) but the synthetic

axial thrust load

47,49 that varies in size on two

gears

10,12.

The

gear

10 and 12 that loads with

axial thrust load

47,49 rests on the bearing support 28 in Fig. 2 left side with

axial vane surface

34 or 36 respectively.26 of the bearing suppories on right side are not affacted the load of the axial thrust load on the gear 10,12.For reduce gear 1-, 12 and the bearing support 28 in Fig. 2 left side between wearing and tearing, load gear with reaction force, this with dashed lines arrow in Fig. 2 illustrates.

In Fig. 3, simplify

bearing support

26,28 and the

gear

10,12 show by first kind of embodiment of the gear machine 1 of Fig. 1 with sectional arrangement drawing.In order to load

gear

10,12 with reaction force, each

gear

10 or 12 be on

axial thrust load

47,49 action directions

axial vane surface

34 and 36 and bearing support 28 and

axial vane surface

34 and 36 opposed

slip surfaces

50 or 52 between, establish a pressure

field.Bearing support

26,28 can as shown in Figure 3ly be configured to be made up of two-part.Pressure field through be presented to respectively in

slip surface

50 and 52

pressure tank

54 or 56 with each

axial vane surface

34 or 36 limited boundaries.Mark through pressure field with double-head arrow simplifiedly among Fig. 3 and affact the

pressure

58,60 on bearing support 28 and the

gear

10,12, wherein, bearing support 28 illustrates

pressure

58,60 and quilt biasing left for clear.Can see the design of

pressure tank

54,56 among Fig. 4.

Fig. 4 shows the

slip surface

50,52 of the spectacle bearing support 28 of Fig. 3 with plan view.First pressure tank 54 is presented in the slip surface around bearing hole 62 ground of Fig. 4 top.Second pressure tank 56 forms around the main part circle of the bearing hole 64 of the bottom in the high-pressure area of the gear machine 1 of Fig. 1.

Pressure tank

54,56 is connected with the high pressure of gear machine 1 via radial groove 66 usefulness pressure mediums.

Gear

10,12 and bearing support 28 load through pressure tank 54 or the 56

usefulness pressure

58,60 that in Fig. 3 and Fig. 4, are presented to respectively in slip surface 50 and 52.

Pressure

58,60 and

axial thrust load

47,49 act in the other direction, therefore reduce sliding friction and the wearing and tearing between

gear

10,12 and bearing support 28.The size of

pressure tank

54,56 is designed at this, and the

axial thrust load

47,49 that is loaded on the

gear

10,12 is compensated through

pressure

58,60 basically, and

gear

10,12 thereby roughly hydrostatic formula ground supporting of quilt.Axial thrust load 49 below the axial thrust load above Fig. 3 47 is greater than is because the pressure tank on the top of Fig. 4 54 structures must be bigger than pressure tank 56 areas of bottom.

Fig. 5 is the plan view by the

axial vane surface

34,36 of second kind of embodiment's of the gear machine 1 of Fig. 1 gear 10,12.At this, pressure field is not through being presented to

pressure tank

54,56 limited boundaries in the bearing support 28 among Fig. 3, but through pressure chamber 68 in the

axial vane surface

34 and 36 that is presented to

gear

10 or 12 respectively or 70 limited boundaries.Pressure chamber 70 at the gear 12 of Fig. 5 middle and lower part is configured to annular groove, and this annular groove is presented in the axial vane surface 36 between the outer surface of the increment face 72 of the tooth 74 of gear 12 and supporting axle 16 around ground.Except correspondence is pressed the annular groove in chamber 79, also have the teeth groove portion section 76 that is presented in the increment face 72 in the pressure chamber 68 of the gear 10 of Fig. 5 middle and upper part, therefore press chamber 68 to be presented in the axial vane surface 34 in large area.Wall 78 with the circumference that centers on gear 10 is radially limiting the border of pressing chamber 68 then.

Press chamber

68,70 for example through being connected with the high pressure of pressure medium with the gear machine 1 of Fig. 1 at the interface slot in bearing support 28 (see figure 1)s.

Through the

pressure chamber

68,70 of

gear

10,12, the

pressure

58,60 of Fig. 3 is applied on the bearing support 28 in the zone of action of the

gear

10,12 that loads with axial thrust load 47,49.Because have the axial pressure acting surface bigger in the pressure chamber 68 on Fig. 4 top, so the pressure that affacts on the upper gear 10 is higher than the pressure chamber of bottom 70.

As alternative, be contemplated that the

pressure chamber

68,70 of Fig. 4 is not to encompass circularly, but encompass part circle and be presented in the

gear

10,12 with having bigger radial width.Therefore for example can simplify manufacturing and dwindle gap leakage, this causes littler hydraulic pressure loss.

At this, the aforementioned axial gap compensation and the mode of action of axial force compensation and the structural type of employed bearing element have nothing to do, and can use at all and be applicable in the structural element of axial seal gear machine.Also be applicable to tooth portion and its parameter as a same reason.This axial clearance compensation and axial force compensation both can have been used in the external gear machine and also can use in the internal tooth turbine.

The gear machine can be used as gear pump or geared engine.

Disclose a kind of gear machine, it is useful on the housing that holds two gears that are engaged with each other.These two gears axially be contained between the bearing support in the housing with axial vane surface supported slidably, in that radially then the supporting axle that is contained in the bearing support of usefulness is supported slidably respectively.When the gear machine moves, hydraulic coupling and mechanical force appear, wherein, the axial thrust load of these power respectively along identical axial action to gear.In order to react on these axial thrust loads, at least one of gear be on the axial thrust load action direction axial vane surface and and the bearing support of said at least one axial vane surface adjacency between be provided with pressure field.

Claims

1. gear machine; Comprise the housing (2) that is used to hold two gears that are engaged with each other (10,12); Said gear utilizes between the bearing support (26,28) of axial vane surface (30,32,34,36) in being contained in housing (2) supported slidably and utilize the supporting axle (8,16) be contained in the bearing support (26,28) supported slidably diametrically respectively in the axial direction; Wherein the axial thrust load (47,49) by the synthetic power of hydraulic coupling that when gear machine (1) moves, occurs and mechanical force affacts on each gear (10,12) along identical axial direction; It is characterized in that, be at least one of gear (10,12) on the action direction of axial thrust load axial vane surface (34,36) and and the bearing support (28) of said at least one axial vane surface (34,36) adjacency between be provided with at least one pressure field.

2. by the described gear machine of claim 1, wherein, said gear (10,12) is made tooth with being tilted.

3. by claim 1 or 2 described gear machines; Wherein, respectively axial vane surface on the action direction that is in axial thrust load of gear (10,12) (34,36) and bearing support (28) and the opposed slip surface of this axial vane surface (34,36) (50,52) between be provided with pressure field.

4. by the described gear machine of claim 3, wherein, said pressure field axially has different acting surfaces along said gear (10,12).

5. by claim 2 or 3 described gear machines, wherein, said pressure field is configured to press chamber (54,56).

6. by the described gear machine of claim 5, wherein, said pressure chamber (54,56) are used as pressure tank (54,56) and are presented in the slip surface (50,52) of the bearing support (28) on the action direction that is in axial thrust load.

7. by the gear machine shown in the claim 6; Wherein, first pressure tank (54) is presented in the slip surface (50,52) of the bearing support (28) on the action direction that is in axial thrust load (47,49) around the clutch shaft bearing hole and second pressure tank (56) is presented in the slip surface (50,52) of the bearing support (28) on the action direction that is in axial thrust load (47,49) with the mode around second bearing hole (64) covering part cyclotomy with one heart (62).

8. by the described gear machine of claim 7, wherein, said pressure tank (54,56) is connected via the high-pressure medium of interface slot (66) with gear machine (1).

9. by the described gear machine of claim 5, wherein, press chamber (68,70) to be presented in the axial vane surface (34,36) on the action direction that is in axial thrust load (47,49) of gear (10,12).

10. by the described gear machine of claim 9, wherein, said pressure chamber (68,70) are along the circumferential sectors ground structure around each supporting axle (8,16) of gear (10,12).

11. by the described gear machine of claim 9, wherein, construct around each supporting axle of gear (10,12) circlewise said pressure chamber (68,70) (8,16).

12. by the described gear machine of claim 11, wherein, at least one presses chamber (68) to be widened, the amplitude of widening is the teeth groove portion section (76) in the increment face (72) of the tooth (74) that is presented to gear (10).

13. it is, wherein, next to pressing chamber (68,70) to carry out the pressure oil supply via the bearing support (28) of adjacency by claim 10 or 11 described gear machines.