CN204004035U - Be used for the device of delivery hydraulic pressure medium - Google Patents
Be used for the device of delivery hydraulic pressure medium Download PDFInfo
- Publication number
- CN204004035U CN204004035U CN201320798204.5U CN201320798204U CN204004035U CN 204004035 U CN204004035 U CN 204004035U CN 201320798204 U CN201320798204 U CN 201320798204U CN 204004035 U CN204004035 U CN 204004035U
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- China
- Prior art keywords
- axial
- motor drive
- drive shaft
- tooth portion
- pump shaft
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D1/101—Quick-acting couplings in which the parts are connected by simply bringing them together axially without axial retaining means rotating with the coupling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The utility model relates to a kind of device (10) that is used for delivery hydraulic pressure medium, and it has electric motor and by the drivable oil hydraulic pump of this electric motor (11).The pump shaft (14) of this oil hydraulic pump (11) is by the cooperation tooth portion (18) of propeller boss connector (20) and motor drive shaft (21) direct-coupling of electric motor.This pump shaft (14) has tooth portion (26), this tooth portion (26) has multiple gear teeth that extend in axial direction (13) respectively, and motor drive shaft (21) has tooth portion (28), this tooth portion (28) has multiple gear teeth (29) that extend in axial direction (13) respectively, the gear teeth (27) of these gear teeth (29) and pump shaft (14) with radial clearance containing intermeshing in tooth portion space (30) of oiling agent.The seal element (35.1) that this tooth portion space (30) is arranged between pump shaft (14) and motor drive shaft (21) by least one seals.
Description
Technical field
The utility model relates to a kind of device that is used for delivery hydraulic pressure medium, and it has electric motor and oil hydraulic pump, and they intercouple by card edge conntecter.
Background technique
Oil hydraulic pump and electric motor are connected with each other by different structural schemes by prior art.In mobile machine for doing work field, especially, in land transport vehicle, often use so-called sliding cross coupling (Oldham-Kupplung), or realize card edge conntecter by driven tooth portion (Mitnehmerverzahnung).Mainly apply coupling at industrial field, it both also all had the cylindrical shaft with feather key respectively at pump side in motor-side, and they are coupled by coupling, and this coupling is provided with suitable feather key-groove.According to the shaft length of motor drive shaft and pump shaft, this structure needs sizable structure space.These coupling have flexible connecting element conventionally.Therefore and be not suitable for high pump dynamic, variable speed and drive except large this shortcoming in structure space, these coupled systems also have following shortcoming according to form of implementation, and they are turnable elastics, and.Sliding cross coupling must be worked for the reason in working life in oil.Therefore, in motor-side, need shaft seal.This means, improved the cost while manufacturing electric motor, and the oil that is arranged in coupler can spill in the time that oil hydraulic pump is installed.
Nowadays used more and more above-mentioned card edge conntecter.Its meets structure space short requirement of trying one's best, and in the time carrying out the driving of variable speed, has met dynamic requirements.At this, pump shaft is usually designed to the outer toothed portion having by the involute tooth portion of DIN or ISO-standard.Motor drive shaft has corresponding internal tooth portion., this system does not possess compensatory coupling element.Oil hydraulic pump conventionally still has shaft seal in this solution; This tooth portion system is not to move in oil sump.The shortcoming of this mode of execution is to make flank wearing and tearing.These wearing and tearing produce by the relative movement on flank.These relative movement are to cause by two axles eccentric position each other, and the trickle augular offset of spin axis by these two axles causes.In gear pump (especially internal gear pump), even can not avoid this augular offset completely in the time the most critically manufacturing motor, pump and connecting element.Pump shaft distortion in the time of hydraulic unit load, and housing parts and lubrication gap also can change their position, and therefore the pump tooth portion of outer gearing is inevitable towards the deviation of motor drive shaft.This deviation inevitably causes the relative movement between corresponding flank.By the sclerosis of specific surface, and material high-intensity by applying, that carry out quenching with Subsequent tempering, these wearing and tearing can be reduced.
In addition, in the time installing first, between outer toothed portion and internal tooth portion, insert certain grease.But in the time that rotating speed is higher, on these link positions, can produce centrifugal force, grease can be dished out and throw outwardly in coupler from tooth portion whereby.This point may cause too early wearing and tearing, until oil hydraulic pump is malfunctioning, and therefore causes the malfunctioning of whole equipment or machine.Advantageously, by the intensification of motor drive shaft and the pump shaft grease of dishing out, this intensification is the wasted power due to electric motor, also due to the frictional work between motor drive shaft and the flank of pump shaft.Therefore, this grease is thin liquid shape, and this contributes to dishing out of grease.
Model utility content
The purpose of this utility model is, a kind of layout of the above-mentioned type is provided, wherein can realize less structure space, and can apply the drive unit (it has avoided above-mentioned shortcoming) of variable speed, especially avoid oiling agent to flow out from tooth portion space or discharge (especially dishing out), therefore can the wearing and tearing between motor drive shaft and pump shaft be down at run duration minimumly, and can realize trouble-free operation at as far as possible long run duration.
This object is so that shockingly simple mode and method are achieved by a kind of device that is used for delivery hydraulic pressure medium, the oil hydraulic pump that this device comprises electric motor and can drive or drive by this electric motor, this oil hydraulic pump has in the axial direction and to extend and round the rotatable pump shaft of pump shaft-spin axis, this pump shaft by propeller boss connector also referred to as patch the cooperation tooth portion of tooth portion and electric motor round (without the additional coupling element) coupling preferably in the axial direction directly or indirectly especially releasably of the rotatable motor drive shaft of motor drive shaft-spin axis, wherein this pump shaft has tooth portion, the gear teeth that this tooth portion extends in the axial direction with multiple difference, and wherein motor drive shaft has tooth portion, the gear teeth that this tooth portion extends in the axial direction with multiple difference, these gear teeth engage with preferably tiny radial clearance with the gear teeth of pump shaft in the tooth portion space of containing oiling agent (especially lubricant grease), and the seal element that wherein this tooth portion space is arranged between pump shaft and motor drive shaft by least one seals.In other words, the utility model refers to, at the pump shaft of preferably outer gearing with between the motor drive shaft of engagement preferably, seal element is set.By this simple Sealing, can avoid up hill and dale the discharge of oiling agent (especially grease) from tooth portion space.Therefore guarantee, even through very long working time, between meshing part, still to there is enough lubricated (especially grease lubrication), the working life of therefore having improved significantly this connector.
Can specify by preferred improvement project, tooth portion seals closely by seal element in space.
Can specify by favourable embodiment, sealing element is made up of the material of rubber elasticity, is preferably made up of elastomer.
Can specify by especially preferred embodiment, sealing element arranges like this and forms, and, except be applied to the elasticity extruding force on pump shaft and motor drive shaft by seal element, does not have mechanical force transmission maybe can be delivered between pump shaft and motor drive shaft.
Sealing element refers to preferred annular seal element aptly, and it is configured to sealing or unremitting, continuous ring.Can specify by preferred improvement project, this annular seal element arranges around pump shaft-spin axis and around motor drive shaft-spin axis.In other words, this annular seal element arranges like this, and pump shaft-spin axis and motor drive shaft-spin axis penetrate annular seal element and extend.
Can specify by favourable structural scheme, this annular seal element is contained in seeing in the axial direction in the axial hole of opening wide of motor drive shaft at least partly or fully outwardly, or be contained in motor drive shaft in the unlimited annular groove of motor drive shaft-spin axis, or this annular seal element is contained in seeing in the axial direction in unlimited hole of pump shaft outwardly, or be contained in pump shaft in the unlimited annular groove of motor drive shaft-spin axis.
Can specify by improvement project, at least one locking-insert is contained on pump shaft and/or on motor drive shaft, and this annular seal element is fixed by this locking-insert, axially from axial hole or annular groove, shifts out preventing.
Additionally or alternatively can specify, motor drive shaft or pump shaft comprise locking element, this locking element is caught from behind annular seal element on the side of the portion of tooth dorsad (in the axial direction) of seal element, fix this annular seal element by this locking element, shift out to ground from axial hole axis preventing.This locking element can for example refer to lock ring, especially refers to clamp ring or refers to clamp ring or thin slice circle.
By especially simple and cost embodiment to one's profit, this annular seal element refers to O-ring seals common on market.This O-ring seals can preferably arrange like this, and it is arranged between the cylindrical diameter on the end of the cylindrical parts of pump shaft and the internal tooth portion of motor drive shaft.The axial locking of this O-ring seals or fixing can realization by the embedded rings on pump shaft, also or by the locking element in motor drive shaft (having corresponding supporting disk) realize.This supporting disk also or insert also can take over so-called " after circle " function.The layout of O shape circle and fixed element realizes like this by especially preferred embodiment, there is no that mechanical force can be delivered between pump shaft and motor drive shaft by these elements.The prestressing force that only has sealing element or these seal elements is the mechanical connection between pump shaft and motor drive shaft.
By favourable improvement project, except O shape circle, annular seal element is configured to molded seal circle.It can be in the region of its axial first end or on its axial first end, has an axial arrangement sealing surface of smooth under non-installment state and/or plane.Alternatively or additionally, this molded seal circle can have cylindrical radial structure sealing surface under non-installment state in the region of its axial the second end or on its axial the second end.By this molded seal circle, can be being used for advantageously sealing in the following manner tooth portion space in the related device of delivery hydraulic pressure medium, described molded seal circle is contained in the free space that this place exists simply.Described free space is as the installing space of molded seal circle, and this molded seal circle is used for sealing tooth portion space.
Can specify by improvement project, molded seal circle has radial flange on its first end, and this radial flange has axial arrangement sealing surface.
Molded seal circle can closely be supported on directly or indirectly on the axial arrangement sealing surface of motor drive shaft by its axial arrangement sealing surface under installment state, and/or molded seal circle can closely be supported on the outer peripheral surface of pump shaft directly or indirectly by its radial structure sealing surface, and/or this molded seal circle has the axial arrangement sealing surface of smooth under installment state not and/or plane in its axial the second end region or on its axial the second end, molded seal circle is supported on directly or indirectly on the axial arrangement sealing surface of pump shaft by this axial arrangement sealing surface under installment state.
Alternatively, molded seal circle can closely be supported on directly or indirectly on the axial arrangement sealing surface of pump shaft by its axial arrangement sealing surface under installment state, and/or molded seal circle can closely be supported on the outer peripheral surface of motor drive shaft directly or indirectly by its radial structure sealing surface, and/or this molded seal circle has the axial arrangement sealing surface of smooth under installment state not and/or plane in its axial the second end region or on its axial the second end, molded seal circle is supported on directly or indirectly on the axial arrangement sealing surface of motor drive shaft by this axial arrangement sealing surface under installment state.
This molded seal circle can in following region, have preferably form as material stacking and make radially add affixed, this region is being arranged at the axial arrangement sealing surface on its axial first end and is being arranged between the radial structure sealing surface on its axial the second end.Therefore can avoid the protuberance of seal ring.
This molded seal circle can have vestibule diaphragm or bellows in following region, and this region is being arranged at the axial arrangement sealing surface on its axial first end and is being arranged between the radial structure sealing surface on its axial the second end.Therefore can improve flexibility or the elasticity of seal ring.By the molded seal circle of such formation, can the relatively large tolerance of balance, and/or can avoid forming large unallowed axial force.
Can specify by improvement project, this annular seal element (especially molded seal circle) has internal diameter, and it or it radial structure sealing surface has or surrounds internal diameter, and this internal diameter is preferably slightly less than the external diameter of pump shaft, or is preferably slightly less than the external diameter of motor drive shaft.
Can specify by structural scheme, this annular seal element (especially molded seal circle) does not have axial length under installment state, this axial length is especially slightly larger than axial spacing (this axial spacing is between the axial end of motor drive shaft and the axial end of putting in contrast of motor drive shaft) in installing space, and annular seal element is arranged in this installing space under installment state.Thereby can reach good axial seal.
Can specify by especially preferred embodiment, molded seal circle has internal diameter in seal ring region, this internal diameter is preferably slightly larger than the relative with sealing collar region of pump shaft or motor drive shaft and the external diameter in the region of putting, the axial arrangement sealing surface of sealing collar region from be arranged at its axial first end region or on its axial first end starts to see in the axial direction through specific axial length and preferably extends to radial structure sealing surface (this radial structure sealing surface is arranged on its axial the second end of region of axial the second end) always, therefore be between molded seal circle and pump shaft or motor drive shaft and form annular space at this.In other words, can and hold the pump shaft of sealing circle or hold between the motor drive shaft of sealing circle in the seal ring region of molded seal circle the annular space unlimited towards the first end of molded seal circle is set.Therefore, molded seal circle can be in sealing collar region under installment state in the axial direction with respect to pump shaft or motor drive shaft without friction or frictionally move without outside, thereby can realize especially good axial seal.
By preferred embodiment, coordinate tooth portion can refer to preferred standard compliant involute tooth portion, especially by least one DIN or SAE standard.
Preferably can apply high temperature resistant and lubricant grease that reduce wear as oiling agent.
Can specify by preferred improvement project, the tooth portion of pump shaft and the toothed portion of motor drive shaft do not carry out surface cure measure, or surperficial hardening thing is set.
By preferred structural scheme, the tooth portion of pump shaft and the toothed portion of motor drive shaft do not have tooth portion-outer surface, and they form or make by scuff-resistant coating respectively.
Can specify by especially preferred embodiment, oil hydraulic pump refers to gear pump, especially refers to internal gear pump.This oil hydraulic pump can preferably comprise the housing being made up of multiple housing parts.The in the situation that of internal gear pump, at least two meshed gears in tooth interlocking region are set in housing, it refers to the small gear of at least one outer gearing and the hollow wheel of engagement at least one.This hollow wheel can preferably support about small gear prejudicially.This small gear is rotatably mounted round spin axis, and hollow wheel is rotatable round the spin axis extending in the axial direction in a circumferential direction.This hollow wheel can have multiple hollow wheel-gear teeth, and they are seen in a circumferential direction and define hollow wheel-backlash.This hollow wheel can have the breach (especially radial indentation) that multiple difference are extended transverse to axial direction in a lateral direction, these breach can lead to respectively in these hollow wheel-backlash, and the outer peripheral surface that these breach can point to towards the radial outward of hollow wheel respectively opens wide.Housing relative with outer peripheral surface hollow wheel and at least one can be set towards the unlimited button of hollow wheel in the housing parts put, be used for hydrostatics and support hollow wheel.
Should be understood that above-mentioned feature and measure can be within the scope of exploitativeness combination in any.
Brief description of the drawings
In further feature of the present utility model, advantage and the requirement of viewpoint accessory rights and the following description book part, draw, wherein described preferred embodiment of the present utility model by accompanying drawing.
Wherein:
Fig. 1 there is shown by device of the present utility model at longitudinal profile, it has card edge conntecter between the pump shaft of oil hydraulic pump and the motor drive shaft of electric motor, and have by the first embodiment by Sealing of the present utility model, and applied O-ring seals and locking insert;
Fig. 2 has illustrated the longitudinal sectional drawing by Fig. 1 in the cross section expanding;
Fig. 3 has illustrated the longitudinal sectional drawing by device of the present utility model in the cross section expanding, and it has card edge conntecter between the pump shaft of oil hydraulic pump and the motor drive shaft of electric motor, and has by the second embodiment's Sealing, and has only applied O-ring seals;
Fig. 4 has illustrated the longitudinal sectional drawing by device of the present utility model in the cross section expanding, and it has card edge conntecter between the pump shaft of oil hydraulic pump and the motor drive shaft of electric motor, and has by the 3rd embodiment's Sealing, and has applied molded seal circle;
Fig. 5 there is shown uninstalled molded seal circle at longitudinal profile;
Fig. 6 there is shown the alternative of uninstalled molded seal circle at longitudinal profile.
Embodiment
Fig. 1 shows the device 10 for delivery hydraulic pressure medium (especially oil), and it comprises oil hydraulic pump 11 and unshowned electric motor, and oil hydraulic pump 11 can be by this electrical motor driven.Oil hydraulic pump 11 has the housing 12 of many bodies.That this housing 12 has is unshowned, also referred to as gas-entered passageway, be used for the suction channel of inhalant liquid piezodielectric, and have unshowned, also referred to as the pressure channel of outlet passageway, hydraulic medium can export under the pressure increasing from this pressure channel.This suction channel and pressure channel one are in unshowned pump chamber.This oil hydraulic pump 11 has the pump shaft 14 extending on axial direction 13, and this pump shaft can be rotated to support in housing 12 round pump shaft-spin axis 15.In an illustrated embodiment, pump chamber is realized by radial axle Sealing 16 towards being sealed between housing parts 12.1 and pump shaft 14 of housing parts 12.1 sides (it illustrates and be preferably configured to flange cap on Fig. 1 left side) of housing 12.It is inserted in the hole 17 of housing parts 12.1.Should be understood that the sealing that also can realize by shaft seal pump chamber, this shaft seal can insert in another housing parts.
This pump shaft 14 is by the cooperation tooth portion 18 also referred to as grafting tooth portion of propeller boss connector 20 and motor drive shaft 21 direct-couplings of electric motor.This motor drive shaft 21 for example can be rotated to support on, in bearing 23 (ball bearing, especially cod) round motor drive shaft-spin axis 22.This bearing 23 is inserted in the hole 24 of bearing support 25 of motor-side.This bearing support 25 for example, is fixedly linked by unshowned interface unit (screw) and the housing parts 21.1 of the housing 12 of oil hydraulic pump 11.
This pump shaft 14 has outer toothed portion 26, this outer toothed portion has multiple gear teeth 27 that extend in axial direction 13 respectively, and motor drive shaft 21 has internal tooth portion 28, this internal tooth portion has multiple gear teeth 29 that extend in axial direction 13 respectively, the gear teeth 27 of these gear teeth 29 and pump shaft 14 with preferably trickle radial clearance containing intermeshing in the tooth portion space 30 of oiling agent.Outer toothed portion 26 fingers of pump shaft 14 are preferably pressed the involute tooth portion of DIN or ISO-standard, and outer toothed portion 28 fingers of motor drive shaft 21 are preferably pressed the suitable involute tooth portion of DIN or ISO-standard.The tooth portion 26 of pump shaft 14 and the tooth portion 28 of motor drive shaft 21 be surface peenings, especially surface peening or nitrogenize.Therefore, on the outer surface of tooth portion 26,28, form respectively wear-resistant layer.Should be understood that these tooth portions alternatively or are extraly provided with the wear-resistant layer of independent coating, this wear-resistant layer is configured to each outer surface of tooth portion.
The lubricant grease that advantageous applications is high temperature resistant and/or reduce wear.
The internal tooth portion 28 of motor drive shaft 21 defines and is arranged on the blind hole 31 of extending in motor drive shaft 21, on axial direction 13, and this blind hole is opened wide outwardly at axial direction 13.Tooth portion space 30 is only one-sided unlimited by this way.
Press the utility model, the seal element that this tooth portion space 30 is arranged between pump shaft 14 and motor drive shaft 21 by least one seals.
In the embodiment shown in Fig. 1 and 2, sealing element refers to O-ring seals common on market 35.1.It has circular cross section under uninstalled (not load) state.It is made up of the elastomer of rubber elasticity.O-ring seals 35.1 is arranged in the axial hole 36 of motor drive shaft 21.This axial hole 36 is opened wide outwardly at axial direction 13.This axial hole 36 radially 54 limits by axial annular wall 37 outwardly, this annular wall around motor drive shaft-spin axis 22 and be columniform and on axial direction 13 extend.This axial annular wall 37 is observed and is had circular cross section in the section perpendicular to motor drive shaft-spin axis 22.This axial annular wall 37 has strutted the internal diameter 38 at axial hole 36.This annular wall 37 has annular wall-width 39 at axial direction 13.
This O-ring seals 35.1 is contained on pump shaft 14, and this pump shaft extends through this O-ring seals on axial direction 13.O-ring seals 35.1 abuts on the cylindrical shaft parts 14.1 of pump shaft 14, and this spindle unit is preferably directly connected on tooth portion space 30.
The so mutual coordination of external diameter 32 of the internal diameter 38 at the axial hole 36 of motor drive shaft 21 and the described spindle unit 14.1 of pump shaft 14, be that difference between internal diameter 38 and internal diameter 32 is less than the external diameter of uninstalled O-ring seals 35.1, or be arranged on the external diameter that radial ringed gap width between the axial annular wall 37 at axial hole 36 and the spindle unit 14.1 of pump shaft 14 of motor drive shaft 21 is less than uninstalled O-ring seals 35.1.Its effect is that O-ring seals 35.1 is (Fig. 1) flexibly extruding or distortion between pump shaft 14 (or spindle unit 14.1) and motor drive shaft 21 (or axial annular wall 37) in the situation that forming elastic reset power under installment state.Therefore, the O-ring seals 35.1 of installation inner side radial seal abut on the described spindle unit 14.1 of pump shaft 14, and outside radial seal abut in the axial annular wall 37 at axial hole 36 of motor drive shaft 21.
Annular wall-the width 39 of the annular wall 37 at the axial hole 36 of motor drive shaft 21 is greater than the installation width 41 of the O-ring seals 35.1 of installation at axial direction 13.Correspondingly, O-ring seals 35.1 under installment state at axial direction 13 fully or in the shaftless axial hole 36 that is contained in motor drive shaft 21 to the annular end face 34 of crossing projectedly motor drive shaft 21 outwardly, this end face is arranged on the free end 33 of motor drive shaft 21.
Axially hole 36 has bottom, ring hole 42, and it has the annular surface 43 extending perpendicular to motor drive shaft-spin axis 22 or in radial direction 54.This O-ring seals 35.1 can abut on surface 43 under installment state, or O-ring seals 35.1 abuts on surface 43 under installment state.
For fear of passing through oil hydraulic pump 11 run durations of electrical motor driven, during pump shaft 14 rotations (based on being rotated by electric motor with the direct-coupled motor drive shaft of pump shaft 14), O-ring seals 35.1 is shifted out outwardly on axial direction 13 from axial hole 36, locking-insert 45 is contained on the described spindle unit 14.1 of pump shaft 14, and pump shaft 14 penetrates this locking-insert and extends (Fig. 1 and 2).
The spindle unit 14.1 of pump shaft 14 can refer to torsion member (Abdrehung).Spindle unit 14.1 is limited by the annular surface 47 of the platform 46 that is connected to the pump shaft parts 14.2 on spindle unit 14.1 of pump shaft 14 on the side in tooth portion 26,28 or tooth portion space 30 at it dorsad at axial direction 13, and this annular surface radially 54 extends outwardly from the outer peripheral surface of spindle unit 14.1.Pump shaft parts 14.2 have external diameter 19, and this external diameter is greater than the external diameter 32 of described spindle unit.
The two is contained in O-ring seals 35.1 and locking-insert 45 in described spindle unit 14.1 and is all arranged in installing space 49, this installing space is limited by the annular surface 43 of the bottom, described hole 42 at axial hole 36 on the one hand, is limited on the other hand by the annular surface 47 of the platform 46 of the pump shaft parts 14.2 of pump shaft 14.Motor drive shaft 21 and pump shaft 14 interfix and are supporting, to prevent the motion in axial direction 13.The annular surface 47 of the annular surface 43 of bottom, hole 42 at the axial hole 36 of motor drive shaft 21 and the platform 46 of the pump shaft parts 14.2 of pump shaft 14 has axial spacing 50 each other.
Locking-insert 45 has external diameter 51, and this external diameter is slightly less than the internal diameter 38 at the axial hole 36 of motor drive shaft 21.This locking-insert 45 has axial Ring Width 52 at axial direction 13, the size of this Ring Width is set like this, be that locking-insert 45 all puts in annular space 53 in all cases, even if locking-insert axially abuts on the ring-shaped platform 46 of pump shaft parts 14.2 of pump shaft 14, this annular space is arranged on the axial annular wall plate 37 at axial hole 36 and the holding between locking-insert 45 and the spindle unit 14.1 of O-ring seals 35.1 of pump shaft 14 of motor drive shaft 21.
Axial spacing 50 between the ring-shaped platform 46 of the bottom 42, radially hole at the axial hole 36 of motor drive shaft 21 and the pump shaft parts 14.2 of pump shaft 14 is selected like this, and O-ring seals 35.1 is not to be axially clipped between the bottom 42, radially hole and locking-insert 45 at axial hole 36 of motor drive shaft 21 at axial direction 13.Therefore guarantee, O-ring seals 35.1 firmly and enduringly seals tooth portion space 30 in radial direction 54.
Fig. 3 shows the second embodiment of the Sealing in tooth portion space, wherein only uses O shape circle 35.1.From shown in Fig. 1 and 2 and the first embodiment described above different, in the second embodiment shown in Fig. 3, omitted locking-insert.Identical member represents with identical reference mark.
In this second embodiment, the spindle unit that is holding O-ring seals 35.1 114.1 of the pump shaft 114 of oil hydraulic pump 11 is seen in the axial direction and is constructed shortlyer than the first embodiment.Spindle unit 114.1 is set size in a second embodiment like this, is provided with little axial clearance 155 limiting from pump side between the ring-shaped platform 46 of this spindle unit 114.1 and the annular end face 34 of motor drive shaft 21.The size of this axial clearance is set littlely at this, so that at the fixing O-ring seals 35.1 of axial direction 13, axially shifts out preventing from the axial hole 36 of motor drive shaft 21.As the first embodiment, the external diameter 19 of the pump shaft parts 14.2 of pump shaft 14 is greater than the internal diameter 38 at the axial hole 36 of motor drive shaft 21 in a second embodiment.But should be understood that at the pump shaft parts described in the first embodiment and the second embodiment and have external diameter, this external diameter is equal to or less than the internal diameter 38 at the axial hole 36 of motor drive shaft 21.In this case, extend in the axial hole 36 of motor drive shaft 21 described pump shaft component axial.
Fig. 4 shows the 3rd embodiment of the Sealing in tooth portion space, has wherein used by molded seal circle 35.2 of the present utility model.Identical member represents with identical reference mark.
Different from the embodiment shown in Fig. 1 to 3, in by the 3rd embodiment of Fig. 4, illustrated pump shaft 214 and by have technology, directly structure and the layout of connected motor drive shaft 221 with it.For realizing the utility model, can not change to adopt or do not change leaving these members.At this, the recess (especially hole or annular groove) for holding Sealing is not set on the free end 33 of motor drive shaft 221.To the intermediate location of its internal tooth portion 28, chamfering or rounding are set at the end face 234 of motor drive shaft 221 at most.Axial spacing 250 between the annular surface 47 of the platform 46 of the described end face 234 of motor drive shaft 221 and the pump shaft parts 14.2 of pump shaft 214 is relatively large, therefore forms sizable free space 255 at this place.
For by the utility model seal tooth portion space 30, in this free space 255, arrange by molded seal circle 35.1 of the present utility model.The latter has at lower the first axial arrangement sealing surface 257 smooth and/or plane of installment state not (not load condition) on its axial first end 256, and on its axial the second end 258, has cylindrical radial structure sealing surface 259 under installment state not.This first axial arrangement sealing surface 257 defines the radial flange 260 of the remaining part extension of radially crossing molded seal circle 35.2 of molded seal circle 35.2.
In the zone line of this molded seal circle 35.2 between its first axial arrangement sealing surface 257 and its radial structure sealing surface 259, have that 54 ground radially extend outwardly radially-affixed 261 of Jia, its form is material stacking.Its effect is in the time that this molded seal circle 35.2 is installed, to prevent the less desirable large radial protrusion of this molded seal circle 35.2 or mounted molded seal circle 35.2.
Molded seal circle 35.2 has internal diameter 263 in seal ring region 262, this internal diameter is preferably slightly larger than the relative with sealing collar region 262 of pump shaft 214 and puts the external diameter 32 of the spindle unit 214.1 of (under the installment state of molded seal circle 35.2), sealing collar region starts preferably extending on radial structure sealing surface 259 on specific axial length at axial direction 13 from its first axial arrangement sealing surface 257 always, is therefore in looping gap 264 (Fig. 4) under the installment state of molded seal circle 35.2 at this.This annular space 264 is preferably constructed to such an extent that open wide towards the first end 256 of molded seal circle 35.2 at axial direction 13.Therefore, the molded seal circle 35.2 of installation can frictionally move or extruding together without friction or without outside with respect to pump shaft 214 in sealing collar region 262 on axial direction 13, thereby can realize especially good axial seal.
This molded seal circle 35.2 is both directly closely supported on the end face 234 also referred to as axial arrangement sealing surface of motor drive shaft 221 under installment state by its first axial arrangement sealing surface 257, be also directly closely supported on the outer peripheral surface of the spindle unit that accommodates molded seal circle 35.2 214.1 of pump shaft 214 by its radial structure sealing surface 259.
Molded seal circle 35.2 has the second axial arrangement sealing surface 265 of smooth under installment state and/or plane on its axial the second end 258.This molded seal circle 35.2 is directly closely supported on the annular surface 47 also referred to as axial arrangement sealing surface of platform 46 of the pump shaft parts 14.2 of pump shaft 214 by the second axial arrangement sealing surface 265 under installment state.
This molded seal circle 35.2 that (i.e. not load) is not installed has axial length 266, and this axial length is more bigger than the axial spacing 250 towards between its annular surface 47 of the platform 46 of the pump shaft parts 14.2 of the annular end of motor drive shaft 221 234 and pump shaft 214.Therefore under the installment state being contained on pump shaft 214, molded seal circle 35.2 is resiliently deformable in the situation that forming axial compression power.Thereby reach good axial seal.
The internal diameter 267 of the radial structure sealing surface 259 of uninstalled molded annular ring 35.2 is more smaller than the external diameter 32 of the spindle unit 214 that is used for holding molded annular ring 35.2 of pump shaft 214.Therefore install, be contained under the state on described spindle unit 214.1, in the case of the axial compression power that is formed on onset on spindle unit 214.1, molded seal circle 35.2 is flexibly out of shape.Thereby reach good radial seal at this place.
Fig. 6 shows the alternative of molded seal circle 35.3, and except the molded seal circle 35.3 shown in Figure 4 and 5, this molded seal circle can be arranged in the free space or installing space between pump shaft 214 and motor drive shaft 21 (by Fig. 4).This alternative molded seal circle 35.3 has annular vestibule diaphragm 268 in zone line between its first axial arrangement sealing surface 257 (it is arranged on its axial first end 256) and its radial structure sealing surface 259 (it is arranged on its axial the second end 258).The annular vestibule diaphragm 268 of uninstalled molded seal circle 35.3 has U-shaped cross-section in the longitudinal sectional drawing shown in Fig. 6.Annular vestibule diaphragm 268 be equipped with radial inward open wide, around annular groove 269.
Molded seal circle 35.2,35.3 shown in Fig. 4 to 6 is made up of the elastomer of rubber elasticity.These molded seal circles 35.2,35.3 are rotational symmetric towards axial medial axis or longitudinal axis under uninstalled state.
Oil hydraulic pump 11 can refer to inner teeth wheel pump, it has the housing 12 being made up of multiple housing parts, at least two meshed gears in tooth mesh regional are set in this housing, they can refer to the small gear of at least one outer gearing, and refer to engagement at least one, preferably with reference to the hollow wheel of this small gear eccentric support.
Reference mark inventory
10 devices
11 oil hydraulic pumps
12 housings
12.1 housing parts/flange cap
13 axial seals
14 pump shafts
14.1 spindle units
14.2 pump shaft parts
15 pump shafts-spin axis
16 (radially) shaft seal
17 holes
18 coordinate tooth portion/grafting tooth portion
19 external diameters
20 propeller boss connectors
21 motor drive shafts
22 motor drive shafts-spin axis
23 bearings/ball bearing/cod
24 holes
25 bearing suppories
26 (outward) tooth portion
27 tooth portions
28 (interior) tooth portion
29 tooth portions
30 tooth portion spaces
31 blind holes
32 external diameters
33 free ends
34 end faces
35.1 O-ring seals
35.2 molded seal circle
35.2 molded seal circle
36 axial holes
37 (radially) annular wall
38 internal diameters
39 annular wall width
40 annular spaces
41 install width
42 bottom, holes
(annular) surface of 43 42
45 locking inserts
46 platforms
47 (annular) surface
48 46 axial arrangement sealing surface
49 installing spaces
50 axial spacings
51 45 external diameter
(axially) Ring Width 53 annular spaces of 52 45
54 radial direction/radially
114 pump shafts
114.1 spindle unit
151 axial spacings
155 axial clearances
214 pump shafts
214.1 spindle unit
221 motor drive shafts
234 221 end face
255 free spaces/installing space
256 axial (first) ends
257 (the first) axial arrangement faces
258 axial (second) ends
259 radial structure sealing surfaces
260 radial flanges
261 radially add affixed
262 seal ring regions
263 262 internal diameter
264 annular spaces
265 (the second) sealing structure faces
266 axial lengths
267 259 internal diameter
268 annular vestibule diaphragm/vestibule diaphragms
269 annular grooves
Claims (27)
1. one kind is used for the device of delivery hydraulic pressure medium, this device comprises electric motor and by the drivable oil hydraulic pump of this electric motor (11), this oil hydraulic pump has at axial direction (13) upper that extend and round the rotatable pump shaft (14 of pump shaft-spin axis (15), 214), the cooperation tooth portion (18) of this pump shaft by propeller boss connector (20) and electric motor round the rotatable motor drive shaft (21 of electric motor-spin axis (22), 221) direct-coupling, wherein this pump shaft (14, 214) there is tooth portion (26), this tooth portion (26) is with multiple gear teeth (27) that above extend at axial direction (13) respectively, and wherein motor drive shaft (21, 221) there is tooth portion (28), this tooth portion (28) is with multiple gear teeth (29) that above extend at axial direction (13) respectively, these gear teeth (29) and pump shaft (14, 214) the gear teeth (27) engage in tooth portion space (30) of containing oiling agent with radial clearance, it is characterized in that, this tooth portion space (30) is arranged at pump shaft (14 by least one, 214) and motor drive shaft (21, 221) seal element (35.1 between, 35.2, 35.3) seal.
2. device according to claim 1, is characterized in that, tooth portion space (30) seals closely by seal element (35.2,35.3).
3. device according to claim 1 and 2, is characterized in that, seal element (35.1,35.2,35.3) is made up of the material of rubber elasticity.
4. device according to claim 1 and 2, is characterized in that, seal element (35.1,35.2,35.3) is made up of elastomer.
5. device according to claim 1 and 2, it is characterized in that, sealing element (35.1,35.2,35.3) arranges like this and forms, except being applied to the extruding force on pump shaft (14,214) and motor drive shaft (21,221) by seal element (35.1,35.2,35.3), not having mechanical force to pass through seal element (35.1,35.2,35.3) and be delivered between pump shaft (14,214) and motor drive shaft (21,221).
6. device according to claim 1 and 2, is characterized in that, seal element (35.1,35.2,35.3) finger ring shape seal element.
7. device according to claim 6, is characterized in that, this annular seal element is configured to the ring of sealing.
8. device according to claim 7, is characterized in that, this annular seal element arranges around pump shaft-spin axis (15) or around motor drive shaft-spin axis (22).
9. device according to claim 8, it is characterized in that, this annular seal element is contained in the axial hole (36) of opening wide outwardly at axial direction (13) of motor drive shaft (21,221) at least partly or fully, or be contained in motor drive shaft in the unlimited annular groove of motor drive shaft-spin axis, or this annular seal element is contained in seeing in the axial direction outwardly in the axial hole of opening wide of pump shaft, or be contained in pump shaft in the unlimited annular groove of motor drive shaft-spin axis.
10. device according to claim 9, it is characterized in that, at least one locking-insert (45) is contained on pump shaft (14) and/or on motor drive shaft, this annular seal element is fixed by this locking-insert, axially from axial hole (36) or annular groove, shifts out preventing.
11. devices according to claim 9, it is characterized in that, motor drive shaft or pump shaft comprise locking element, this locking element is caught from behind annular seal element on the side of tooth portion (in the axial direction) dorsad, fix this annular seal element by this locking element, shift out to ground from axial hole axis preventing.
12. devices according to claim 11, is characterized in that, this locking element refers to lock ring.
13. devices according to claim 11, is characterized in that, this locking element refers to thin slice circle.
14. devices according to claim 6, is characterized in that, this annular seal element refers to O-ring seals (35.1).
15. devices according to claim 6, it is characterized in that, this annular seal element is molded seal circle (35.2,35.3), this molded seal circle has the axial arrangement sealing surface (257) of smooth under installment state not and/or plane in its axial first end region or on its axial first end (256), and in its axial the second end region or on its axial the second end (258), has cylindrical radial structure sealing surface (259) under installment state not.
16. devices according to claim 15, it is characterized in that, molded seal circle (35.2,35.3) has radial flange (260) on its first end (256), and this radial flange has axial arrangement sealing surface (257).
17. devices according to claim 15, it is characterized in that, molded seal circle (35.2, 35.3) under installment state, be closely supported on directly or indirectly on the axial arrangement sealing surface (234) of motor drive shaft (221) by its first axial arrangement sealing surface (257), and/or molded seal circle (35.2, 35.3) be closely supported on directly or indirectly on the outer peripheral surface of pump shaft (214) by its radial structure sealing surface (259), and/or this molded seal circle (35.2, 35.3) in its axial the second end region or on its axial the second end (258), there is the second axial arrangement sealing surface (265) of smooth under installment state not and/or plane, molded seal circle (35.2, 35.3) under installment state, be supported on directly or indirectly on the axial arrangement sealing surface (47) of motor drive shaft (214) by this axial arrangement sealing surface.
18. devices according to claim 15, it is characterized in that, molded seal circle is closely supported on directly or indirectly on the axial arrangement sealing surface of pump shaft by its axial arrangement sealing surface under installment state, and molded seal circle is closely supported on the outer peripheral surface of motor drive shaft directly or indirectly by its radial structure sealing surface, and/or this molded seal circle has the axial arrangement sealing surface of smooth under installment state not and/or plane in its axial the second end region or on its axial the second end, molded seal circle is supported on directly or indirectly on the axial arrangement sealing surface of motor drive shaft by this axial arrangement sealing surface under installment state.
19. devices according to claim 15, it is characterized in that, molded seal circle (35.2) has and radially adds affixed (261) in following region, and this region is positioned at and is arranged on the first axial arrangement sealing surface (257) on its axial first end (256) and is arranged between the radial structure sealing surface (259) on its axial the second end (258).
20. devices according to claim 19, is characterized in that, this radially adds affixed (261) and is configured to material stacking.
21. devices according to claim 15, it is characterized in that, molded seal circle (35.3) has vestibule diaphragm (268) or bellows in following seal ring region, and sealing collar region is positioned at and is arranged on the first axial arrangement sealing surface (257) on its axial first end (256) and is arranged between the radial structure sealing surface (259) on its axial the second end (258).
22. devices according to claim 15, it is characterized in that, can and hold the pump shaft (214) of sealing circle or hold between the motor drive shaft of sealing circle that in the seal ring region (262) of molded seal circle (35.2,35.3) annular space (264) unlimited towards the first end (256) of molded seal circle (35.2,35.3) being set.
23. devices according to claim 1 and 2, is characterized in that, this cooperation tooth portion (18) refers to involute tooth portion.
24. devices according to claim 1 and 2, is characterized in that, this oiling agent refers to lubricant grease resistant to elevated temperatures, that reduce wear.
25. devices according to claim 1 and 2, is characterized in that, the tooth portion (28) of the tooth portion (26) of this pump shaft (14,214) and motor drive shaft (21,221) is surface cure.
26. devices according to claim 1 and 2, is characterized in that, the tooth portion of this pump shaft and the tooth portion of motor drive shaft have tooth portion-outer surface, and they are respectively arranged with the wear-resistant layer of independent coating.
27. devices according to claim 1 and 2, it is characterized in that, this oil hydraulic pump (11) refers to internal gear pump, it has the housing (12) being made up of multiple housing parts, at least two meshed gears in tooth mesh regional are set in this housing, they refer to the small gear of at least one outer gearing, and refer to engagement at least one, with reference to the hollow wheel of this small gear eccentric support.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE202013104531U DE202013104531U1 (en) | 2013-10-07 | 2013-10-07 | Hydraulic pump and electric motor with sealed direct connection |
| DE202013104531.4 | 2013-10-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204004035U true CN204004035U (en) | 2014-12-10 |
Family
ID=49668397
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320798204.5U Expired - Fee Related CN204004035U (en) | 2013-10-07 | 2013-12-05 | Be used for the device of delivery hydraulic pressure medium |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN204004035U (en) |
| DE (1) | DE202013104531U1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110259838A (en) * | 2019-07-09 | 2019-09-20 | 太仓市海谷五金机电设备有限公司 | A kind of oil pump power input structure |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102014202281A1 (en) * | 2014-02-07 | 2015-08-13 | Bühler Motor GmbH | Oil pump drive |
| DE102014202696B4 (en) * | 2014-02-14 | 2018-12-27 | Bayerische Motoren Werke Aktiengesellschaft | Device for transmitting torque in a range extender |
| DE102016225196C5 (en) * | 2016-12-15 | 2024-03-21 | Baumüller Nürnberg GmbH | Electric motor oil pump |
-
2013
- 2013-10-07 DE DE202013104531U patent/DE202013104531U1/en not_active Expired - Lifetime
- 2013-12-05 CN CN201320798204.5U patent/CN204004035U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110259838A (en) * | 2019-07-09 | 2019-09-20 | 太仓市海谷五金机电设备有限公司 | A kind of oil pump power input structure |
Also Published As
| Publication number | Publication date |
|---|---|
| DE202013104531U1 (en) | 2013-10-24 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141210 Termination date: 20171205 |
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| CF01 | Termination of patent right due to non-payment of annual fee |