CN101443578B

CN101443578B - Low noise gear pump

Info

Publication number: CN101443578B
Application number: CN2007800168725A
Authority: CN
Inventors: J·A·奥布赖恩二世
Original assignee: Limo Reid Inc
Current assignee: Limo Reid Inc
Priority date: 2006-03-13
Filing date: 2007-03-13
Publication date: 2012-10-10
Anticipated expiration: 2027-03-13
Also published as: JP2009530530A; WO2007106500A2; EP1994308A2; WO2007106500A3; CN101443578A; BRPI0708783A2; JP5068306B2

Abstract

A low noise gear set (300) for use generally and preferably with a power plant (11) having an engine (12) driving a pump (16) connected to a low pressure fluid source (18), generating high pressure fluid at an output (107, 252, 254). The idle gear (312) meshes with the drive gear (310) along two points (314, 316) of the profile (318, 320) of the corresponding gears (310, 312). The first point (314) being the root (326) of one gear tooth meshing with the tip (328) of the opposite gear tooth creating an initial first contact point (314) and a subsequent second point (316) along the profile (318, 320) when the teeth are disengaging at the first point (314) and engaging at the second point (316), forming a sealed area (322), allowing the fluid (324) to hydrostatically escape between the points (314, 316).

Description

Low noise gear pump

The cross reference of related application

The application is that the U. S. application sequence number submitted on February 22nd, 2006 is 11/359728 part continuity application, and sequence number is that this U. S. application of 11/359728 provisional application of requiring to submit on February 22nd, 2005 number is 60/655221 preference.Patent application serial numbers is that 11/359728 application is that the U. S. application sequence number submitted on April 8th, 2005 is 11/101837, is 7179070 part continuity application now for U.S. Patent number, and sequence number is that to require the provisional application sequence number of submission on April 9th, 2004 be 60/560897 preference for this U. S. application of 11/101837.

It is 60/781775 rights and interests that the application requires in the U.S. Provisional Application sequence number that on March 13rd, 2006 submitted to.

Background of invention

The present invention relates generally to automotive power, and relates to the low noise gear pump of reduction gear wear for use in any system particularly.

Gear pump and motor are some the most durable obtainable pumps.Yet the noise that these pumps produce is undesirable for many application.It is desirable controlling this noise source.Noise rank and frequency receive the influence of wheel tooth type, wheel tooth geometrical shape, wheel tooth surface and lubrication.When wheel tooth meshed, the oil that is stranded between them had produced most of noise.

In many instances, can damage in the geometrical shape of revising wheel tooth under the situation of ability of gear transmission load, can not change the type or the level and smooth tooth surface of used wheel tooth.In addition, but use full-bodied oil and grease attenuating noise, but can not be applicable to each gear unit well.

Therefore, expectation provides a kind of low noise gear pump that reduces gear wear extraly.

Summary of the invention

For quiet seal strategy is provided, have to rethink the gear mode of engagement at present.Replace the gear that uses the profile of tooth side to seal; The top of use gear obtains sealing for the root of gear as a point; And when next wheel tooth engaged, oil overflowed from hydrostatic ground (hydrostatically) between the previous meshed gears tooth.

The present invention is preferably and comprises the low noise gear set that is used for any device, and is described as being used for power plant in this article, and these power plant have motor, and its driving is connected to the pump on the lowpressure stream body source, to produce high-pressure liquid in the outlet; At least one variable displacement pump/motors, it responds said high-pressure liquid to rotate in the outlet; This discharge capacity pump/motor comprises actuation gear and the idler gear that is meshed with this actuation gear, and wherein, this idler gear is meshed with actuation gear along two points of the flank profil of said corresponding gear; At least one point in two points is the root of a wheel tooth; It is meshed with relative top of wheel tooth and has produced first contact points that is used between root and top, obtaining with the sealing of lowpressure stream body source phase fluid; And when indented joint along second point subsequently of flank profil, in case fluid is overflowed on hydrostatic ground when being disengaged between these 2 in the high-pressure liquid outlet.

Preferably, be used to provide the method for the low noise gear pump that reduces gear wear to comprise the steps: to provide first gear; Make first gear first in two contact pointss locate to engage second gear; Wherein, first contact points is the root of a wheel tooth and the relative top of wheel tooth, and second contact points be the point along gear-profile one side, and its point with relative gear-profile one side is meshed; When the some place of gear in two contact pointss engages, be formed for sealing the zone of wheel tooth; And be disengaged along flank profil another some place in these two contact pointss of the turning gear gear teeth, the method that fluid static(al) ground is overflowed is provided.

Description of drawings

When combining accompanying drawing to consider, those skilled in the art according to following detailed description of preferred embodiment will easily understand above the present invention and other advantage, in the accompanying drawing:

Fig. 1 a is the schematic representation according to hydraulic hybrid power system of the present invention, and wherein the model selection valve is in ＂ driving ＂ position;

Fig. 1 b is the view of the hydraulic hybrid power system of Fig. 1 a, and wherein the model selection valve is in ＂ neutral gear ＂ position;

Fig. 1 c is the view of the hydraulic hybrid power system of Fig. 1 a, and wherein the model selection valve is in ＂ reverse gear ＂ position;

Fig. 1 d is the view of the hydraulic hybrid power system of Fig. 1 a, and wherein the model selection valve is in ＂ Parking ＂ position;

Fig. 1 e is the view of the hydraulic hybrid power system of Fig. 1 a, and wherein brake override (override) device is in override position;

Fig. 2 is the magnification ratio schematic representation of drive motor shown in Fig. 1 a-1d and displacement control device;

Fig. 3 is the magnification ratio schematic representation of brake override device shown in Fig. 1 a-1d and check valve bridge circuit;

Fig. 4 is the perspective exploded view according to internal gear pump/motor of the present invention;

Fig. 5 is the partial, exploded perspective view according to external gear pump/motor of the present invention; And

Fig. 6 is the zoomed-in view according to gear engagement apparatus and method of the present invention.

Embodiment

Following patent application is incorporated herein by reference: U.S. Provisional Application sequence number 60/560897; U.S. Patent Application Serial Number 11/101837, promptly present U.S. Patent number 7179070; U. S. Patent provisional application sequence number 60/655221; U. S. application sequence number 11/359728; And U. S. Patent provisional application sequence number 60/781775.

Low noise gear set 300 is described as being used for pump/motor 16; And motor 76a-76d for example is preferably the co-assigned submitted on April 8th, 2005 and co-pending patent application sequence number 11/101837, the variable displacement pump/motors shown in the present U.S. Patent number 7179070 just, and sequence number is the disclosure of this application of 11/101837 so incorporates into by reference and shown in Fig. 4 and Fig. 5.As alternative, pump/motor 16 is leaf type or piston type variable displacement pump/motors with motor 76a-76d or is the fixed displacement pump/motor.In addition; The pump/motor 16 that has low noise gear set 300 can combine hydraulic hybrid power system 10 to use together; The co-assigned of for example submitting on February 22nd, 2005 is the hydraulic hybrid power system shown in 11/359728 with common pending application sequence number, and sequence number is that therefore the disclosure of this application of 11/359728 is incorporated into and shown in Fig. 1-3 by reference.

Referring now to Fig. 6,, refers to according to low noise gear set of the present invention with 300 generally.Low noise gear set 300 can be used on expectation and uses in the various equipments of internal gear pump/motor or external gear pump/motor of any viscous fluid, thereby has advantageously provided the low noise that is used for any environment and the gear train of low wearing and tearing.

Low noise gear set 300 comprises two or more at least gears, is preferably actuation gear 310 and idler gear 312.When driving idler gear 312, idler gear 312 is at two points, 314, the 316 place's mesh driving gears 310 along counterpart profile 318,320.When actuation gear 310 rotated, gear 310,312 engaged at first contact points, 314 places.This first contact points 314 preferably forms in top 328 (this moment is for being positioned at the wheel tooth top 328 on the idler gear 312) time that roots 326 (this moment is for being positioned at the wheel tooth root 326 on the actuation gear 310) of a wheel tooth engage relative wheel tooth.

When actuation gear 310 was rotated further, preferably the side along the relative gear-profile 320 of gear-profile of actuation gear 310 318 and idler gear 312 formed second contact points 316.When first contact points 314 breaks away from during gear rotates and second contact points 316 when engaging subsequently, through produced sealing 322 by the mechanical pressure that pressure fluid or gas produced that is positioned at pump 16 1 sides.A spot of fluid 324 is trapped in like oil and is between actuation gear 310 and the idler gear 312 by point 314 and put between the 320 formed sealings 322.Because sealing 322 forces the center of the pressure of retentate fluid 324 perpendicular to gear 310,312, thereby force fluid 324 between gear 310,312, to flow out, rather than gear 310,312 is attempted to compress the fluid 324 between them.

When use comprises the power plant of hydraulic hybrid power system 10 (comprising pump/motor 16) for example, be used to provide the method for optimizing that reduces gear wear and be used for the low noise gear set 300 of pump 16 to comprise the steps:

First gear 310 is provided;

Make first gear 310 engage second gear 312 at first contact points, 314 places, wherein, first contact points 314 is the top 328 of root 326 with the relative wheel tooth of a wheel tooth;

Make first gear 310 engage second gear 312 at second contact points, 316 places, wherein, second contact points 316 is the point along gear-profile 318 1 sides, and this point is meshed with point along relative gear-profile 320 1 sides;

When gear 310,312 breaks away from second contact points, 316 joints and with first contact points 314, be formed for sealing the zone 322 of wheel tooth; And

In case when being disengaged wheel tooth, then provide to be used to method that fluid 324 hydrostatic ground are overflowed at first contact points, 314 places.

When actuation gear 310 rotated idler gear 312, the engagement of wheel tooth formed first contact points 314 and second contact points 316 subsequently constantly.Like this, when second contact points 316 was disengaged, first contact points subsequently on the wheel tooth formed at the root and the place, top of respective teeth subsequently.The rotation of gear provides the mesh point system along gear-profile.When engaging second contact points 316 initial first contact points 314 begin break away from, formed the zone 322 that is used to seal.In case first contact points 314 breaks away from, then fluid 324 hydrostatic ground overflow sealing area 322.

Referring now to Fig. 1 a,, refers to hydraulic hybrid power system with 10 generally.Power system 10 can be used in the various equipments, such as but not limited to motor vehicle that those skilled in the art understood, ship, submarine, helicopter etc., but in for the sake of clarity below the present invention, describing, is regarded as being installed in the motor vehicle.Power system 10 comprises power setting part 11, mode selector module 43, control section 59 and power transport portion 76.

The power setting part 11 of power system 10 comprises the motor 12 that is communicated with fuel source 14.Motor 12 can be conventional internal-combustion engine, turbo machine, be provided with the electric motor, fuel cell etc. of power by battery.Motor 12 is provided to moment of torsion selectively and is preferably variable-displacement hydraulic pump/motor 16, and wherein, variable displacement hydraulic pump/motor 16 is provided with the low pressure source 18 of hydraulic fluid and is provided with high pressure pipe line 20 at its outlet side at its inlet side.In the time of within remaining on scope of the present invention, hydraulic fluid can be liquid, such as but not limited to water, hydraulic fluid, transmission fluid etc., or belong to any compressible gas in the scope of the invention.Because install 16 according to the patterns of system 10 alternately as pump or motor, so be pump/motor 16, below it is carried out more detailed description with this unit describe.

The power setting part 11 of system 10 comprises a plurality of accessory drives, and these accessory drives include but not limited to motor generator set 22, air conditioning compressor 24 and heat pump 26.Motor generator set 22 is connected on the power maintenance module 28, and power maintenance module 28 is connected on the battery 30.Heat pump 26 is communicated with heater core (heater core) 32, and heat pump 26 and heater core 32 the two all be communicated with cooling water source 34 fluids of motor 12.Air conditioning compressor 24 is communicated with heat exchanger 36.

Accessory drives

22,24 and 26 preferably motor or the oil hydraulic motor through is separately moved.As alternative,

accessory drives

22,24 and 26 selectively mechanically clutch be connected on the motor 12.Accumulator 38 is communicated with high pressure pipe line 20 fluids that pump/motor 16 exports.Accumulator 38 is used as the liquid-storage container of high pressure hydraulic fluid, and keeps the high pressure in the system 10, for example, and through (not shown) superchargings such as use pressurized gas, like what those skilled in the art understood.

Throttling control module 40 receives the input signal of accumulator 38 via the input signal of the adjusting of the signal admission of air on circuit 24a compressor 24, via the input signal of the reception of the signal on circuit 28a power maintenance module 28 and via the signal on the circuit 38a.As going through hereinafter, based on circuit 24a, the input signal on 28a and the 38a, throttling control module 40 on circuit 42, provide the output signal with control motor 12 and pump/motor 16 one of them or the two.Signal on

circuit

24a, 28a, the 38a and 42 can be electronic signal or the machine feedback between each member and the throttling control module 40.Throttling control module 40 can be any suitable mechanical device or electric device, and these devices are exercisable, to control the operation of motor 12 and pump/motor 16 based on one or more inputs.

Mode selector module 43 comprises the model selection valve 44 that is communicated with high pressure pipe line 20 fluids through high pressure entry pipeline 46.Model selection valve 44 is preferably and is connected on speed variator type stick (not shown) etc., selectively valve 44 is moved on to one of following positions: " D " or activation point (preferably see Fig. 1 a), " N " or neutral position (preferably seeing Fig. 1 b), " R " or reverse gear position (preferably seeing Fig. 1 c) and " P " or Parking position (preferably seeing Fig. 1 d).Model selection valve 44 comprise be connected on it, the low-pressure inlet pipeline 48 adjacent with high pressure entry pipeline 46.Model selection valve 44 also comprises high-pressure outlet pipeline 50 and the low tension outlet pipeline 52 that is connected on it, is positioned at model selection valve 44 relative sides.As going through hereinafter, each position P, R, N and the D of model selection valve 44 be selectively with the interior section of position and

pipeline

46,48,50 and 52 alignment, and the direction of flow of hydraulic fluid in the control system 10.Although be described as " inlet " and " outlet " above, all can be used as inlet or outlet according to the operating conditions of system 10 at each

pipeline

46,48,50 and 52 of run duration, this will go through following.

Pipeline

50 and 52 is connected on the brake override device 54 successively.Brake override device 54 also comprises and is positioned at brake override device 54 relative sides, is connected to high-pressure outlet pipeline 56 and low tension outlet pipeline 58 on it.Brake override device 54 has primary importance or normal position 54a and the second place or override position 54b, and this will be described in greater detail below.

Control section 59 comprises the displacement control valve 60 that is communicated with high pressure pipe line 20 fluids through high pressure entry pipeline 62.Displacement control valve 60 comprise be connected on it, the low-pressure inlet pipeline 64 adjacent with high pressure entry pipeline 62.Displacement control valve 60 also comprises high-pressure outlet pipeline 66 and the low tension outlet pipeline 68 that is connected on it, is positioned at displacement control valve 60 relative sides.Displacement control valve 60 is for unsteady normal valve and comprise the accelerator 70 and break 72 that is connected on it, so that will guide to a plurality of

cylinder

74a, 74b, 74c and 74d from the stream of displacement control valve 60.Accelerator 70 is preferably on the accelerator pedal and brake pedal (not shown) that is mechanically connected to separately with break 72.Break 72 is connected on the brake override device 54 via connector 73.Displacement control valve 60 has primary importance or quickens position 60a, the second place or holding position 60b and the 3rd position or decelerate position 66c.Each

position

60a, 60b and the 60c of displacement control valve 60 all aligns interior section and the

pipeline

62,64,66 and 68 of each

position

60a, 60b and 60c selectively, and controls the direction of the flow of hydraulic fluid of leading to

cylinder

74a, 74b, 74c and 74d, preferably sees Fig. 2.

Each

cylinder

74a, 74b, 74c and 74d are mechanically connected to each driving or

traction motor

76a, 76b, 76c and 76d (in power transport portion 76) on each wheel via

connector

75a, 75b, 75c and 75d.Motor 76a-76d is preferably variable displacement motor.For example through being connected on wobbler or the like, the discharge capacity of motor 76a-76d has been confirmed in the position of connector 75a-75d as understood by one of ordinary skill in the art.High-pressure outlet pipeline 66 is communicated with a side liquid of piston (not shown) among each cylinder 74a-74d, and a side liquid relative with piston is communicated with among low tension outlet pipeline 68 and the cylinder 74a-74d.Have a plurality of

traction motor

76a, 76b, 76c and 76d though system 10 is depicted as, it will be appreciated by those skilled in the art that to adopt within the scope of the invention and lack to a motor.For example, in single motor equipment of motor vehicle, the output of single-motor is connected on the differential gear, and this differential gear is mechanically connected on the pair of driving wheels.Each

traction motor

76a, 76b, 76c and 76d have upper end-

hole

77a, 77b, 77c and 77d and

lower end mouth

78a, 78b, 78c and 78d.The direction of the fluid stream of process upper end-hole 77a-77d and lower end mouth 78a-78d has been confirmed the direction of motor 76a-76d.Feedback connector 80 extends between the piston of displacement control valve 60 and cylinder 74a-74d.

Check valve bridge circuit 82 comprises a plurality of

safety check

84,86,88 and 90, and to arrange with the similar mode of full-wave bridge rectifier, preferably sees Fig. 3.Pipeline 92 is communicated with the inlet of safety check 84 and the outlet fluid of safety check 86.Pipeline 92 also is communicated with high-pressure outlet pipeline 56 fluids.Pipeline 94 is communicated with the inlet of safety check 86 and the inlet fluid of safety check 88.Pipeline 94 also is communicated with low pressure source 18 fluids of hydraulic fluid.Pipeline 96 is communicated with the outlet of safety check 88 and the inlet fluid of safety check 90.Pipeline 96 also is communicated with low tension outlet pipeline 56 fluids.Pipeline 98 is communicated with the outlet of safety check 84 and the outlet fluid of safety check 90.Pipeline 98 also is communicated with high pressure pipe line 20 fluids.

Referring now to Fig. 4,, refers to according to inner gearing of the present invention with 100 generally.As understood by one of ordinary skill in the art, device 100 can be configured to move as motor or pump, but in of the present invention describing below, will be called motor.Internal gear motor 100 comprises the hollow casing 102 with base portion 104 and end cap 106.Base portion 104 defines recess or cavity 108 therein, and its sized becomes to receive first axle 110 and first piston parts 112.End cap 106 comprises at least two port ones 07 (only illustrating), and each port one 07 all extends between the internal surface and outer surface of end cap 106, preferably on the relative both sides of end cap 106.One of them port one 07 is connected on the high pressure section such as the high pressure pipe line 20 among Fig. 1 a-1e of fluid system, and another port one 07 then is connected on the fluid source 18 among return line or fluid source such as Fig. 1 a-1e.

First axle 110 defines and runs through the hole 114 that its base portion 111 extends, and comprises upper surface 113 upwardly extending first outward flanges 116 and a plurality of isolated second outward flanges 118 from base portion 111.Inward flange 120 extends upward from the base portion 111 of first axle 110, and is positioned to adjacent with hole 114.First outward flange 116 is positioned to adjacent with hole 114.The two is all spaced apart for second outward flange 118 and hole 114 and inward flange 120.First seal sleeve, 122 sized become to be assemblied in rotationally in the hole 114; And preferred in height with the base portion 111 of first axle 110 about equally; To such an extent as to when sleeve 122 placed hole 114, the upper surface 113 of the upper surface of sleeve 122 and base portion 111 was substantially flush.

The external gear 124 of approximate circular cross-section is suitable for being arranged on the upper surface 113 of base portion 111, and wherein, the respective curved internal surface of the crooked outer surface of gear 124 and outward

flange

116 and 118 is adjacent.External gear 124 comprises a plurality of teeth 126 that are formed on its internal surface.When placing 113 last times of upper surface, gear 124 axially is fixed between outward flange 118 and the inward flange 120.

The internal gear 128 of approximate circular cross-section comprises formation a plurality of teeth 130 on its outer surface, and defines the hole 132 that wherein connects.Tooth 130 is exercisable, in order to be formed on external gear 124 internal surfaces on tooth 126 be meshed.The lower surface of gear 128 extends into sleeve 122 and rotates with this sleeve 122, and wherein, when assembling and operation motor 100, tooth 130 cooperates with respective teeth on the sleeve 122, like the more detailed description of hereinafter.The outer surfaces of the tooth 130 of internal gear 128 is adjacent with the internal surface of inward flange 120.When assembling motor 100, hole 132 is suitable for receiving the free end of live axle or output shaft 134.Internal gear 128 can axially move along axle 134.Live axle 134 is bearing in the end cap 106 like ball bearing, roller bearing etc. through bearing 135.The upper surface that the free end of live axle 134 exceeds end cap 106 extends intended distance and as the output shaft of motor 100.

Second piston element 136 defines hole 138 on the portion part within it, and is suitable for being installed on the

outward flange

116 and 118 respective upper surfaces of first axle 110.Therefore, second piston 136 is installed in respectively on the upper surface and lower surface of lower spindle 110 with first piston 112.

Second axle 140 is suitable for being arranged in the hole 138 of second piston element 136, and defines the hole 142 that is used to receive live axle 134 on portion's part within it.Second axle 140 comprises that to the flange that extends below 144 it cooperates with first axle, 110 upwardly extending inward flanges 120 when assembling motor 100.Upper spindle 140 comprises the pair of holes 146 that wherein connects, to be communicated with gear 122 and 124 fluids at motor 100 run durations.

Second seal sleeve 148 comprises a plurality of teeth 150 that are formed on its outer surface, and defines the hole 152 that wherein connects.As going through hereinafter; Second seal sleeve 148 is suitable in hole 152, receiving upper spindle 140; And be suitable for being contained in the external gear 124 and therewith rotate, wherein when assembling and when moving motor 100, tooth 126 cooperates with tooth 150 on the sleeve 148.

When assembling motor 100, first axle 110 places base portion 104, the first seal sleeves 122 of housing 102 to place axle 110 with first piston 112, and external gear 124 places on the axle 110.The internal gear 132 and second axle 138 are installed on the live axle 134, and are assembled into and make the

respective teeth

130 and 126 of gear 132 and 124 mesh rotationally and internal gear 132 engages with first seal sleeve 122.Second piston 136 is attached on the upper surface of axle 110, and second seal sleeve 148 places on second axle 138 and with external gear 124 and engages.Cooperate with upwardly extending inward flange 120 to the flange that extends below 144, be divided into the inlet and discharge chamber of motor 100 with inside, and upper end cap 106 is attached on the base portion 104 with enclosing housing 102 external gear.Flange 120 and 144 radially extends between tooth 126 and tooth 130, forms inlet and discharges the chamber in the opposite side formation of flange with the side at flange.

During operation, axle 134 is connected on the load (not shown), for example wheel etc.Compression fluid is for example introduced from the high pressure pipe line 20 of Fig. 1 a-1e from fluid system through one of them port one 07; Inlet's side of leading to gear 124 and 128 through hole 146; Act on engaging

tooth

126 and 130 with transmitting gear and axle, between each tooth, flow to arrive and discharge the chamber and be discharged to another port 107 through another hole 146.First seal sleeve 122 is providing the rotary seal and second seal sleeve 148 between the external gear 124 and second axle 140, rotary seal to be provided between the internal gear 128 and first axle 110, to guarantee inlet and the integrity of discharging the

chamber.Need Sealing

122 and 148 to keep fluid-tight and allow effective operation of motor 100 according to 100 in motor of the present invention.

Spatial relationship normal or acquiescence between the tooth 126 of gear 124 and the tooth 130 of gear 128 makes roughly whole axial area of soldered tooth of tooth 126 and 130.In this relation, motor 100 produces its maximum volume flow or maximum output.Because internal gear 128 can axially move along axle 134, so can advantageously change from its maximum pump discharge according to motor 100 of the present invention.When internal gear 128 when first axle 110 moves, tooth 126 engages with tooth 130 less axial area, this has reduced the volume flow or the discharge capacity of motor 100.

When unit 100 is configured to motor; External pressure source (for example from the hydraulic fluid of external hydraulic pump, from pressurized air in the air compressor etc.); The volume flow of leading to port one 07 is provided, with turn gear 124 and 128 and on axle 134, produce output torque.When variation in pressure, internal gear 128 will move along the axis of axle 134, to change the shaft horsepower of motor 100.Motor 100 can be advantageously used in control output rpm under the output loading that extensively changes, and these output loadings include but not limited to motor vehicle, gun turret, big machinery, bulldozer, machinery machine, boats and ships, agricultural machinery equipment etc.

When unit 100 is configured to the pump of low speed or low moment of torsion ground rotatingshaft 134 and prime mover (the for example motor 12 among Fig. 1 a-1e); Pump 100 will be exported through change it based on the internal pressure in the pump case 102, thereby input speed or the input torque that reduces worked.In this case, output port 107 will produce higher back pressure in discharging the chamber, and internal gear 128 will move to along the axis of axle 134 along this axis, gear 128 and be in or near the point of balance, to continue operation.Therefore, pump 100 can change to internal gear 128 and the roughly adjacent minimum injection rate of lower spindle 110 from internal gear 128 maximum output or the maximum pump discharges roughly adjacent with upper spindle 140.

Referring now to Fig. 5,, refers to according to outer gearing of the present invention with 200 generally.As understood by one of ordinary skill in the art, device 200 can be configured to move as pump or motor, but will be called pump in order to simplify description of the invention.External gear pump 200 comprises hollow casing 202, and this housing 202 has first end cap 204 and second end cap 206 that is connected by body portion 208.Preferably, first end cap 204 and second end cap 206 are attached on the body portion 208 like high-strength bolt etc. through a plurality of fastening pieces 210.Body portion 208 defines recess 212 therein.

Second gear 218 that is formed with a plurality of teeth 220 on first gear 214 that is formed with a plurality of teeth 216 on its outer surface and its outer surface is suitable for being arranged in the recess 212 of housing 202.At the run duration of pump 200, respective gears 214 and 218 tooth 216 and 220 are exercisable, with engagement rotationally in recess or pump chamber 212.First gear 214 has from axle 222, the second gears 216 of its extension and has the multidiameter shaft 224 from its extension.First gear 214 is fixed on the axle 222, and second gear 218 can axially move along axle 224.Axle 222 and 224 extends on opposite axial direction, and spools 224 on length greater than axle 222.First seal sleeve 226 with internal tooth receives first gear 214, and second seal sleeve 228 with internal tooth receives the end of second gear 218.

Board-like assembly parts 230 comprise from it to the flange that extends below 232, and are being attached on its flat upper surfaces on first thrust plate 234.Preferably, thrust plate 234 is attached on the assembly parts 230 like high-strength bolt etc. through a plurality of fastening pieces 236.The free end of axle 222 extends through the hole that is formed in assembly parts 230 and the thrust plate 234.Axle 222 free end is fastened in assembly parts 230 and the thrust plate 234 through a pair of nut 238 rotationally, and by bearing 240 like ball bearing, roller bearing etc. and rotatably support.Second seal sleeve 228 is exercisable, to be contained in the assembly parts 230 in the recess adjacent with flange 232.When axle 222 was installed in assembly parts 230 and the thrust plate 234, gear 214 was axially fixing with respect to housing 202.

Second thrust plate 242 is attached on the upper surface 205 of first end cap 204 like high-strength bolt etc. through a plurality of fastening pieces 244.Plate 242 comprises the free-ended hole that is used for receiving axes 224 and the bigger hole that is used to receive and locate first seal sleeve 226 of contiguous first end cap, 204 upper surfaces.Axle 224 free end extends through the hole in the plate 242, in ladder place and a pair of nut 246 threaded joint, and by bearing 248 like ball bearing, roller bearing etc. and rotatably support.In the cavity 250 of bearing 248 preferred arrangements in being formed at first end cap, 204 upper surfaces 205, and nut 246 is attached to axle 224 on the end cap on the lower surface opposite with upper surface 205.The lower surface that axle 224 free end surpasses end cap 204 extends intended distance, and as the live axle or the output shaft of pump 200.

Body portion 208 defines all first port 252 and second port 254 that extends between the surface and outer surface within it.A port in the port 252 and 254 is connected to the low pressure stage of fluid system such as the hydraulic fluid source 18 among Fig. 1 a-1e etc., and the another port in the port 252 and 254 then is connected to the high pressure section of fluid system or the high pressure pipe line 20 among pressurized segment such as Fig. 1 a-1e.

In when operation, axle 224 is connected on prime mover, for example the motor 12 among Fig. 1 a-1e etc.When prime mover rotatingshaft 224, gear 218 rotates and causes gear 214 to rotate.Fluid is introduced from fluid system through one in the port 252 or 254, is trapped between engaging tooth 216 and 220 as well known in the art, and through another discharge in the port 252 or 254.At the run duration of pump 200, in housing 202, form suitable path and correctly transmit to guarantee fluid.First seal sleeve 226 is providing the rotary seal and second seal sleeve 228 between second gear 218 and assembly parts 230, rotary seal to be provided between first gear 214 and the upper surface 205, to guarantee the integrity of pump chamber 212.200 of pump in accordance with the present invention need seal sleeve 226 and 228 to keep sealing and allow pump 200 to move effectively.

Normal or default space relation between gear 214 and 218 the tooth 216 and 220 makes roughly whole axial area of soldered tooth of tooth 216 and 220.In such relation, pump 200 produces its maximum volume flow or maximum pump discharge.Because second gear 218 can axially move along axle 224, so pump in accordance with the present invention 200 can advantageously change from its maximum pump discharge.When second gear 218 when lower thrust plate 242 moves, tooth 216 and 220 less axial area engage, this has reduced the volume flow or the discharge capacity of pump 200.Usually, this will take place during with low speed or low moment of torsion ground rotatingshaft 224 at prime mover, and pump 200 will be through changing its output based on the internal pressure in the pump case 202, thereby input speed or the input torque that reduces worked.In this case, output port 252 or 254 will produce higher back pressure in recess 212, and second gear 218 will move to along the axis of axle 224 along this axis, gear 218 and be in or near the point of balance, to continue operation.Therefore, pump 200 can change to gear 218 and the roughly adjacent minimum injection rate of lower thrust plate 242 from gear 218 maximum output or the maximum pump discharges roughly adjacent with assembly parts 230.

When device 200 is configured to motor; External pressure source (for example from the hydraulic fluid of external hydraulic pump, from pressurized air of air compressor etc.) provides the volume flow of leading to port 252 and 254, with turn gear 214 and 218 and on axle 224, produce output torque.When variation in pressure, second gear 218 will move along the axis of axle 224 to change the shaft horsepower of motor 200.Motor 200 can be advantageously used in control output rpm under the output loading that extensively changes, and these loads include but not limited to motor vehicle, gun turret, big machinery, bulldozer, machinery machine, boats and ships, agricultural equipment etc.

When operational system 10, motor 12 starts and to pump/motor 16 moment of torsion is provided, and pump/motor 16 provides the hydraulic fluid of pressurization to high pressure pipe line 20.Accumulator 38 guarantees that the hydraulic pressure in the pipeline 20 keeps relative stability, and with mode known in those skilled in the art the energy storage is provided.Propagation of pressure in the pipeline 20 is to

pipeline

46,62 and 98.

Referring to Fig. 1 a; When model selection valve 44 is in D or activation point and brake override device 54 and is in the 54a position; The hydraulic fluid pipeline 46 of will flowing through; Direction shown in the arrow is through model selection valve 44 and flow out pipeline 50 in the D position, and the direction shown in the arrow and arrives the corresponding upper end-hole 77a-77d of motor 76a-76d through brake override device 54 and flow out pipeline 56 in the 54a position; Process motor 76a-76d also arrives corresponding lower end mouth 78a-78d, thereby has reduced pressure and for each motor 76a-76d the output torque along forward direction is provided with mode known in those skilled in the art.Low pressure hydraulic fluid among the lower end mouth 78a-78d is advanced via pipeline 58; Direction shown in the arrow is through brake override device and flow out pipeline 52 in the 54a position, and the direction shown in the arrow is through model selection valve 44 and flow out pipeline 48 and arrive hydraulic fluid source 18 in the D position.

Referring to Fig. 1 b, when model selection valve 44 is in N or neutral position and brake override device 54 and is in the 54a position, the hydraulic fluid pipeline 46 of will flowing through, but owing to stop this fluid model selection valve 44 of flowing through at N position and pipeline 46 adjacent end

caps.Outlet conduit

50 and 52 with pipeline 48 in the low pressure hydraulic fluid phase fluid be communicated with, and since pressure and the pressure in

pipeline

52 and 58 in the

pipeline

50 and 56 balance each other, so thereby do not have a flow through brake override device 54 or flow to motor 76a-76d of fluid.When in the N position, if any needs oil stream among the motor 76a-76d, then the oil from liquid-storage container 18 can be used for flowing through motor 76a-76d.

Referring to 1c; When model selection valve 44 is in R or reverse gear position and brake override device and is in the 54a position; The hydraulic fluid pipeline 46 of will flowing through; Pass through model selection valve 44 and flow out pipeline 52 along the direction shown in the arrow in the R position, pass through brake override device 54 and flow out pipeline 58, and arrive the corresponding lower end mouth 78a-78d of motor 76a-76d along the direction shown in the arrow in the 54a position; Process motor 76a-76d also arrives corresponding upper end-hole 77a-77d, thereby has reduced pressure and be provided at the output torque on the inverse direction with mode known in those skilled in the art for each motor 76a-76d.Low pressure hydraulic fluid among the lower end mouth 77a-77d is advanced through piping 56; Direction shown in the arrow is through brake override device and flow out pipeline 50 in the 54a position, and in the D position direction shown in the arrow through model selection valve 44 and flow out pipeline 48 and arrive hydraulic fluid source 18.

Referring to Fig. 1 d; When model selection valve 44 is in P or Parking position and brake override device 54 and is in the 54a position and since in the P position with each

pipeline

46,48; 50 and 52 adjacent end caps have stoped and have flowed to flowing arbitrarily of motor 76a-76d; So the

hydraulic fluid pipeline

46,48 of will can not flowing through, any pipeline in 50 and 52.

As stated, in primary importance 54a, brake override device 54 allows hydraulic fluid flowing (this depends on the position of model selection valve 44) between

pipeline

50 and 56 and between pipeline 52 and 58.But in second place 54b, preferably see Fig. 1 e and since in second place 54b with each pipeline 50; 52,56 and 58 adjacent end caps have stoped the mobile arbitrarily of process brake override device 54, the pipeline 46 so hydraulic fluid will can not be flowed through; Any pipeline in 48,50 and 52.Through break 72 actuate and signal along the transmission of connector 73, brake override device 54 moves on to second place 54b from its normal primary importance 54a, and stops hydraulic fluid to flow to motor 76a-76d from displacement control valve 44.

When operation; If break 72 engages when model selection valve 44 is in D or activation point; And override 54 moves to second place 54b; The only hydraulic fluid source that then the is used for motor 76a-76d check valve bridge circuit 82 of flowing through, so all fluids stream all pass through check valve bridge circuit 82 transmission.During braking, motor 76a-76d will begin advantageously during braking, from the rotation of wheel, to recapture energy as pump.When braking in the D position, hydraulic fluid will from hydraulic fluid source 18 flow through pipeline 94, through safety check 86, through piping 92, arrive upper end-hole 77a-77d and arrive motor 76a-76d, in motor 76a-76d, increased hydraulic fluid pressure.Then; High pressure hydraulic fluid will from motor 76a-76d flow through lower end mouth 78a-78d, through piping 96; And if the pressure in the pipeline 96 flows to pipeline 20 and recharges accumulator 38 at this high pressure hydraulic fluid greater than the pressure in the pipeline 98 then can pass through safety check 90 and get into pipeline 98.

When braking when being in the R position at model selection valve 44; Hydraulic fluid will from hydraulic fluid source 18 flow through pipeline 94, through safety check 88, through piping 96, arrive lower end mouth 78a-78d and arrive motor 76a-76d, in motor 76a-76d, increased hydraulic fluid pressure.The high pressure liquid baric flow then will from motor 76a-76d flow through upper end-hole 77a-77d, through piping 92; And if the pressure in the pipeline 92 flows to pipeline 20 and recharges accumulator 38 at this high pressure hydraulic fluid greater than the pressure in the pipeline 98 then can pass through safety check 84 and get into pipeline 98.

In case check valve bridge circuit 82 is used to prevent that hydraulic fluid flows to motor 76a-76d along inverse direction when vehicle from stopping fully.When braking and model selection valve 44 when being in the D position, brake override device 54 is shifted to position 54b and is prevented flowing from model selection valve 44 to motor 76a-76d.To attempt to arrive motor 76a-76d from the stream of high pressure pipe line 20, but stop it to flow to motor via safety check 84 and 90 via pipeline 98.Check valve bridge circuit 82 will only allow to flow to pipeline 98 or flow to pipeline 98 from pipeline 96 via safety check 90 through safety check 84 from pipeline 92, and this will be only just can take place when perhaps the pressure in the pipeline 58 and 96 is greater than the pressure in the pipeline 98 with 92 at pipeline 56.If the pressure in the pipeline 92 is less than the pressure in pipeline 98 and the pipeline 94, then safety check 86 will be opened, but because pipeline 94 is in low pressure, so flowing from liquid-storage container 18 to pipeline 92 can not taken place.Similarly; If the pressure in the pipeline 96 is less than the pressure in pipeline 98 and the pipeline 94; Then safety check 88 will be opened; But because pipeline 94 is in low pressure, thus mobile from liquid-storage container 18 to pipeline 96 can not take place, and prevented that advantageously high pressure hydraulic fluid causes motor 76a-76d to engage along inverse direction after vehicle stops fully.

When operation, hydraulic fluid is controlled with break 72 via the accelerator 70 that is connected on the displacement control valve 60 by the operator through flowing of system 10.Connector 80 and connection set 75a-75d link together via suitable connection etc., and this allows motor 76a-76d the mode of control to be provided and to displacement control valve 60 feedback to be provided via connection set 75a-75d to motor 76a-75d through connecting 75a-75d to be similar to connector 80.

For example, if the vehicle user (not shown) is pushed accelerator 70, this causes feedback connector 80 to move and cause displacement control valve 60 60a moves towards the position along acceleration direction.From the high-pressure liquid of pipeline 62 port on the displacement control valve 60 of will flowing through, increased the pressure in the pipeline 66 and flowed to cylinder 74a-74d.Because the pressure in the pipeline 66 will be greater than the pressure in the pipeline 68, thus connector 75a-75d will move along acceleration direction, thereby the discharge capacity that has increased motor 76a-76d has also increased the output torque of motor 76a-76d.

In case reach the required output torque of motor 76a-76d, motor 76a-76d moves connector 75a-75d with throttling back along deceleration direction, reduces the pressure in the pipeline 66 and increases the pressure in the pipeline 68.This feedback connector 80 that moves through transmits back displacement control valve 60, and displacement control valve is shifted to position 60b.The 60b in the position, through the flowing of displacement control valve 60, thereby connector 75a-75d keeps static, thereby and the discharge capacity of motor 76a-76d keep constant its output torque to keep constant.

If the user removes his or her pin from accelerator 70, this causes feedback connector 80 to move along deceleration direction, and causes displacement control valve 60 to shift to position 60c.From the high-pressure liquid of pipeline 62 port on the displacement control valve 60 of will flowing through, increased the pressure in the pipeline 68 and flowed to cylinder 74a-74d.Because the pressure in the pipeline 68 so connector 75a-75d will move along deceleration direction, has reduced the discharge capacity of motor 76a-76d, thereby has reduced the output torque of motor 76a-76d greater than the pressure in the pipeline 66.

Advantageously, between accelerator 70 and motor 12, directly do not connect.Opposite is; Move and control motor 12 based on engine speed (based on the signal on the circuit 42), moment of torsion (based on the position of displacement control valve 60, this position receives accelerator 70 position effects) and the combination of system pressure (based on the signal on the circuit 38a).The throttling control module 40 of this input combination permission system 10 makes motor 12 always with its peak efficiencies operation based on known engine efficiency parameter, and therefore the proportional control to motor 12 and system 10 is provided.When the complete supercharging of system 10, can advantageously kill engine 12, instantaneous fuel consumption is reduced to zero.When system pressure descended, motor 12 was reset to pipeline 20 pressure to be provided once more.

Situation or running state (as determined) based on air conditioning compressor 24, power maintenance module 28 and accumulator 38 by the corresponding signal on its

circuit

24a, 28a and the 38a; Throttling control module 40 is sent signal on circuit 42, with the discharge capacity of starting or shutting engine down 12 and/or change pump/motor 16.

When the system pressure in the pipeline 20 increased, accumulator 38 was full of and has reduced the flow rate from pump/motor 16.Owing to lead to the output of motor 76a-76d, the stream of pump/motor 16 continues to reduce and descends until system pressure.When if the flow of pump/motor 16 reaches zero delivery at any one time, then motor 12 can cut out up to needing flow once more.If fixture needs power to prevent motor 12 stall (clutch of supposition fixture is connected on the motor 12), then also can reduce the flow of pump/motor 16.Power transporting system 10 obtains its efficient through the speed of average power consumption.Intermittent bursts situation (intermittent burst) energy needed is supplied with by the energy of storage in the accumulator 38.The flow that pump/motor 16 provides is greater than the required mean flowrate of powered vehicle.So the added flow that is produced by pump 16 is stored in the accumulator 38.

Hydraulic hybrid power system 10 according to the present invention has advantageously provided uncomplicated and simple and clear controlling method; In case and rely on the discharge capacity of motor 76a-76d to increase then its output torque response with regard to the very fast fact, for system 10 provides responsiveness better controlled method.

Those skilled in the art will appreciate that; System 10 according to the present invention can be used for to the system of any amount hydraulic power being provided; These systems include but not limited to be used for the propulsion system of naval vessels (for example, steamer, ship or submarine) floating or diving, the propulsion system of helicopter etc.In brief, the output of pump/motor 16 can be used with power system 10, so that be oil hydraulic motor such as motor 76a-76d that the purpose of any amount is moved any amount when keeping belonging to the scope of the invention.

When keeping belonging to the scope of the invention; Connector 73,75a-75d and 80 and

circuit

24a, 28a, 38a and 42 on signal can be mechanical connector such as hydraulic pipe line, cable, metallic rod of any type etc., or the electrical signal of communicating by letter with solenoid valve etc.

According to the regulation of patent statute, through the present invention that regarded as the content description of representing its preferred embodiment.But should be noted that do not breaking away under its spirit and the situation of scope that the present invention also can be through the alternate manner realization shown in removing specifically.

Claims

1. a pump gear group (300) comprising:

Actuation gear (310) has a plurality of drive gear teeth; With

Idler gear (312); Have a plurality of idler gear teeth that are meshed with said drive gear teeth, wherein, said driving and idler gear (310; 312) be initially at along counterpart profile (318; 320) first contact points (314) in two contact pointss (314,316) locate to mesh and subsequently second contact points (316) in two contact pointss locate engagement, with at said driving and idler gear (310; Sealing area (322) is provided 312); Be engaged on first and second contact pointss (314,316) simultaneously and sentence retentate fluid (324) in sealing area (322), and when said first contact points (314) when locating to be disengaged the pressure through retentate fluid (324) perpendicular to driving and idler gear (310; 312) center makes fluid (324) the hydrostatic ground that is detained overflow sealing area (322), and wherein said first contact points (314) comprises the top (328) of the root (326) and the relative wheel tooth in said driving and the idler gear of a wheel tooth in said driving and the idler gear.

2. pump gear group according to claim 1 (300); It is characterized in that; Said two contact pointss (314; 316) second contact points in comprises along second contact points (316) of a gear-profile (318) one sides, when said driving and idler gear (310,312) when engaging rotationally; Said second contact points (316) along a said gear-profile (318) one sides is meshed with second contact points (316) along relative gear-profile (320) one sides when being disengaged in first contact points (314) of first contact points (314) of said root (326) and said top (328), with the sealing area (322) that is formed for sealing said wheel tooth.

3. pump gear group according to claim 2 (300) is characterized in that, said sealing area (322) provides and has been used for said first contact points (314) when said wheel tooth makes fluid (324) hydrostatic ground overflow when being disengaged mechanism.

4. low noise gear set (300) of using with power plant (11), said power plant (11) comprising:

Motor (12), its driving are connected to the pump (16) on the lowpressure stream body source (18), to locate to produce high-pressure liquid in output (107,252 and 254);

At least one variable displacement pump/motors (16), it responds said high-pressure liquid to locate to rotate in output (107,252 and 254);

Said discharge capacity pump/motor (16) comprising:

Actuation gear (310) has a plurality of drive gear teeth; With

Idler gear (312) has a plurality of idler gear teeth that are meshed with said drive gear teeth, wherein; Said driving and idler gear (310; 312) initially locate engagement in first contact points (314) along each flank profil (318,320) of said driving and idler gear, with said lowpressure stream body source (a 18) fluid-tight; Subsequently before said first contact points (314) is located to be disengaged; Flank profil (318,320) along each gear of said driving and idler gear is located engagement in second contact points (316), with in first and second contact pointss (314; 316) forming sealing area (322) between comes retentate fluid (324) in sealing area (322); And before said first contact points (314) was located to be disengaged, the pressure through retentate fluid (324) was perpendicular to driving and the center of idler gear (310,312) makes fluid (324) the hydrostatic ground that is detained spill into the output (107 of said high-pressure liquid from sealing area (322); 252 and 254); Wherein said first contact points (314) is the root (326) of a wheel tooth, and said root (326) is meshed with the top (328) of relative wheel tooth and produces first make contact, between said root (326) and said top (328), to obtain the fluid-tight with said lowpressure stream body source (18).

5. low noise gear set according to claim 4 (300); It is characterized in that; Said second contact points (316) comprises along second contact points (316) of a gear-profile (318) one sides; When being disengaged, the point of said second contact points (316) along a said gear-profile (318) one sides in the point of said root (326) and said top (328) engage with second contact points (316) along relative gear-profile (320) one sides; Form the zone (322) that when said gear (310,312) engages, is used to seal said wheel tooth.

6. low noise gear set according to claim 5 (300) is characterized in that, said sealing area (322) provides and has been used for mechanism that fluid (324) hydrostatic ground is overflowed.

7. one kind is used for comprising through the hydrostatic bearing between the contact surface of gear (300) is applied the gear train that power reduces wearing and tearing:

At least two gears (310,312), wherein; Said at least two gears (310,312) are along at least two contact pointss (314 of counterpart profile (318,320); 316) engagement and one after the other; So that sealing area (322) to be provided at least, be engaged on said at least two engagements (314 simultaneously between said two gears (310,312); 316) sentence retentate fluid (324) in sealing area (322); And when first contact points (314) in said at least two contact pointss (314,316) when locating to be disengaged the pressure through retentate fluid (324) perpendicular to driving and the center of idler gear (310,312) makes fluid (324) the hydrostatic ground that is detained overflow sealing area (322)

, first contact points (314) in wherein said at least two contact pointss (314,316) comprises the top (328) of the root (326) and the relative wheel tooth of a wheel tooth.

8. gear train according to claim 7 (300); It is characterized in that; Said at least two contact pointss (314; 316) second contact points (316) in comprises along second contact points (316) of a gear-profile (318) one sides; Said second contact points (316) along a gear-profile (318) one sides is meshed with second contact points (316) along relative gear-profile (320) one sides when said root (326) point and said top (328) point are disengaged, to form the zone (322) that is used to seal said wheel tooth when said at least two gears (310,312) joint.

9. gear train according to claim 8 (300) is characterized in that, said sealing area (322) provides and has been used for mechanism that fluid (324) hydrostatic ground is overflowed.

10. method that is used for when reducing gear wear, providing low noise gear pump (300), said method comprises:

A., first gear (310) with a plurality of wheel teeth and second gear (312) with a plurality of wheel teeth are provided;

B. make one root and another first contact points (314) at top in the wheel tooth of said first gear (310) in comprising wheel tooth locate to engage second gear (312);

C. make said one gear-profile (318) one sides and another second contact points (316) of gear-profile (320) one sides in the wheel tooth of said first gear (310) in comprising wheel tooth locate to engage said second gear (312) subsequently; With form sealing area (322) be trapped between said first and second contact pointss (314,316) fluid (324) and

D. locate to be disengaged said wheel tooth in said first contact points (314); Pass through thus perpendicular to first and second gears (310; The pressure at center 312) makes fluid (324) the hydrostatic ground that is detained overflow said sealing area (322), and wherein first contact points (314) comprises the top (328) of the root (326) and the relative wheel tooth of a wheel tooth.