Fundamentals of designing hydraulic gear machines

Jarosław Stryczek

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ISBN/ISSN:

978-83-01-21145-5

DOI:

Wydawnictwo:

Wydawnictwo Naukowe PWN

Rok wydania:

2020

Liczba stron:

353

XML:ISBN/ISSN:

ONIX MARC21

Bibliografia:

Stryczek, Jarosław. Fundamentals of designing hydraulic gear machines. Red. . : Wydawnictwo Naukowe PWN, 2020, 353 s. ISBN 978-83-01-21145-5

Bibliografia refWorks:

RT Book, Whole

SR Electronic(1)

A1 Stryczek, J.

T1 Fundamentals of designing hydraulic gear machines

PB Wydawnictwo Naukowe PWN

YR 2020

SN 978-83-01-21145-5

Bibliografia BibTex:

@Book{ 225073, author = "Stryczek, Jarosław", editor = "", title = "Fundamentals of designing hydraulic gear machines", publisher = "Wydawnictwo Naukowe PWN", year = "2020", address = "", isbn = "978-83-01-21145-5" }

Bibliografia endNote:

TY - BOOK

AU - Stryczek, Jarosław

ED -

TI - Fundamentals of designing hydraulic gear machines

PB - Wydawnictwo Naukowe PWN

CY -

PY - 2020

SN - 978-83-01-21145-5

ER -

Netografia (standard APA):

Stryczek, Jarosław. Fundamentals of designing hydraulic gear machines [baza danych online] : Wydawnictwo Naukowe PWN, 2020 [dostęp: 24 08 2024]. Dostęp w Ibuk Libra: https://libra.ibuk.pl/reader/fundamentals-of-designing-hydraulic-gear-machines-jaroslaw-stryczek-225073.

HGM, hydraulic, gear, machines

Hydraulic gear machines (HGM) are a type of machines applied in the hydraulic drive and control systems where gears are the main unit both in terms of the design and operation principle. HGMs are utilized for converting mechanical energy into hydr...

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ISBN/ISSN:

978-83-01-21145-5

DOI:

Wydawnictwo:

Wydawnictwo Naukowe PWN

Rok wydania:

2020

Liczba stron:

353

XML:ISBN/ISSN:

ONIX MARC21

Preface 12
1. Definition, systematics and methodology of designing hydraulic gear machines 14
1.1. Definition and systematics14
1.2. Designing methodology16
2. The process of energy transformation in hydraulic gear machines 21
2.1. General models of a pump and a motor21
2.1.1. General model of a pump21
2.1.2. General model of a motor22
2.2. Ideal and real characteristics of a pump and a motor25
2.2.1. Characteristics of a pump25
2.2.2. Characteristics of a motor29
2.3. Conclusions33
3. Gears in hydraulic gear machines 34
3.1. Teeth, gears and the external involute gear systems35
3.1.1. The tooth, the external gear35
3.1.2. The boundary number of teeth, correction of the external tooth39
3.1.3. The external involute gear system41
3.1.3.1. The uncorrected gear system, the principle of co-operation, t e number of contact41
3.1.3.2. The corrected gear system, the principle of co-operation, the number of contact43
3.2. Teeth, gears and the internal involute gear systems46
3.2.1. The tooth, the internal gear46
3.2.2. The boundary number of teeth, correction of the internal tooth48
3.2.3. The internal involute gear system49
3.2.3.1. The uncorrected gear system, the principle of co-operation, the number of contact49
3.2.3.2. The corrected gear system, the principle of co-operation, the number of contact51
3.2.3.3. Interference of the gear teeth53
3.3. Teeth, gears and the internal cycloidal gear systems55
3.3.1. Teeth, gears and the uncorrected internal epicycloidal gear system55
3.3.2. Teeth, gears and the corrected internal epicycloidal gear system60
3.3.3. Principle of co-operation in the epicycloidal gear system, the line of contact, the number of contact62
3.3.4. Teeth, gears and the uncorrected internal hypocycloidal gear system65
3.3.5. Teeth, gears and the corrected internal hypocycloidal gear system68
3.3.6. Principle of co-operation in the hypocycloidal gear system, the line of contact, the number of contact70
3.3.7. Principle of co-operation in the cycloidal gear system with moveable axes72
3.3.8. Principle of co-operation in the cycloidal multi-gear systems75
3.4. Conclusions76
4. Channels and clearances in the fluid power gear machines79
4.1. The system of fixed channels and clearances79
4.2. The system of moveable channels and clearances81
4.3. The system of channels and clearances in the machines of the first group82
4.3.1. Inlet channel and inlet chamber83
4.3.2. Inlet bridge84
4.3.3. Outlet channel and outlet chamber86
4.3.4. Outlet bridge87
4.3.5. Axial and radial clearance104
4.4. The system of channels and clearances in the machines of the second group106
4.4.1. Inlet channel and inlet chamber106
4.4.2. Inlet bridge109
4.4.3. Outlet channel and outlet chamber110
4.4.4. Outlet bridge111
4.4.5. Axial and radial clearance119
4.5. The system of channels and clearances in the machines of the third group121
4.5.1. Inlet channel and inlet chamber122
4.5.2. Inlet bridge123
4.5.3. Outlet channel and outlet chamber125
4.5.4. Outlet bridge126
4.5.5. Axial and radial clearance133
4.6. The system of channels and clearances in the machines of the fourth group135
4.6.1. The system of channels and clearances in the multifunctional hydraulic gear machine (MHGM)135
4.6.2. The system of channels and clearances in the ORBIT orbital motor138
4.6.3. The system of channels and clearances in the MAX orbital motor with double cycloidal gearing141
4.7. Conclusions143
5. Delivery and delivery pulsation, capacity and capacity pulsation of the fluid power gear machines 145
5.1. General formulae146
5.1.1. Instantaneous delivery146
5.1.2. The proper, theoretical and average delivery153
5.2. Delivery and delivery pulsation in the machines of the first group155
5.1.3. Delivery pulsation155
5.3. Delivery and delivery pulsation in the machines of the second group161
5.4. Delivery and delivery pulsation in the machines of the third group164
5.4.1. Epicycloidal gear machines166
5.4.2. Hypocycloidal gear machines173
5.5. Delivery of the machines of the fourth group180
5.6. Conclusions182
6. Pressure and pressure pulsation in the fluid power gear machines 183
6.1. Theoretical characteristics of the pressure and pressure pulsation changes in the intertooth displacement chamber T in the machines od the first-third group185
6.2. Theoretical characteristics of the pressure and pressure pulsation changes in the intertooth displacement chamber in the machines of the fourth group192
6.3. Conclusions194
7. The visual study of the flow processes and phenomena taking place in the channels and clearances of the gear machines196
7.1. General comments196
7.2. The subject and methodology of the visual study; the test stand196
7.3. The visual study of the machines of the first group200
7.3.1. Inlet channel and inlet chamber203
7.3.2. Inlet bridge205
7.3.3. Outlet channel and outlet chamber207
7.3.4. Outlet bridge208
7.3.5. Relief grooves in the outlet bridge zone213
7.3.6. Axial clearance217
7.4. The visual study of the machines of the second group218
7.4.1. Inlet channel and inlet chamber220
7.4.2. Inlet bridge222
7.4.3. Outlet channel and outlet chamber223
7.4.4. Outlet bridge224
7.5. The visual study of the machines of third group227
7.5.1. Inlet channel and inlet chamber229
7.5.2. Inlet bridge231
7.5.3. Outlet channel and outlet chamber236
7.5.4. Outlet bridge237
7.6. Conclusions239
8. Pressure study in the channels and clearances of the gear machines242
8.1. The subject and methodology of the study; the test stand242
8.2. Study of the pressure in the channels and clearances of the machines of the first group243
8.2.1. Study of gear pump I without axial clearance compensation243
8.2.2. Study of gear pump II with axial clearance compensation252
8.3. Study of the pressure in the channels and clearances of the machines of the second and third group259
8.4. Conclusions272
9. Designing the housings of the fluid power gear machines274
9.1. Methodology of designing the housings of the fluid power gear machines274
9.2. Determining the design and technological requirements for the housings of the pumps275
9.3. Determining the basic shape of the pumps276
9.4. Strength analysis of the housings of the basic shape gear pumps with the use of FEM279
9.4.1. Geometrical models, load and fixation279
9.4.2. Numerical models, research programme281
9.4.3. Results of the strength analysis of the basic shape pump housings283
9.5. Global and local modification of the basic shape housing286
9.6. Strength analysis of the housings of the modified shape gear pumps with the use of FEM288
9.7. Assumption of the final shape of the pumps289
9.8. Conclusions290
10. Designing the axial clearances compensation system 292
10.1. Principle of axial clearance compensation. Methodology of designing the axial clearance compensation system292
10.2. Designing the axial clearance compensation system in the machines of the first group294
10.2.1. Assumption of a design solution for the compensation system294
10.2.2. Defining area Ap of the pressure working in the axial clearance, and the division of the area into partial areas Api295
10.2.3. Defining the distribution of partial pressure pi working on partial areas Api297
10.2.4. Defining partial repulsive forces Fpi and the total repulsive force Fp299
10.2.5. Defining partial torques of the repulsive forces Mpi and total torque of the repulsive forces Mp300
10.2.6. Defining points of application xpi, ypi of partial repulsive forces Fpi and point of application xp, yp of total repulsive force Fp306
10.2.7. Shaping total compensation area Ac and its division into partial areas Aci. Determining of compensation pressure pc306
10.2.8. Defining partial compensation forces Fci and total compensation force Fc309
10.2.9. Defining coordinates xci, yci of the points of application of partial compensation forces Fci and coordinates xc, yc of the points of application of total compensation force Fc309
10.2.10. Comparison of total repulsive force Fp and its point of application xp, yp with total compensation force Fc and the point of its application xc, yc311
10.3. Designing the axial clearance compensation system in the machines of thesecond group312
10.3.1. Assumption of a design solution for the compensation system312
10.3.2. Defining partial repulsive forces Fpi and total repulsive force Fp313
10.3.3. Defining points of application xpi, ypi of partial repulsive forces Fpi and point of application xc, yc of total repulsive force Fp317
10.3.4. Shaping the total compensation area Ac and its division into partial areas Aci. Determining of compensation pressure pc320
10.3.5. Defining partial compensation forces Fci and coordinates xci, yci of the points of its application and total compensation force Fc and coordinates xc, yc of the point of its application322
10.3.6. Comparison of total repulsive force Fp and its point of application xp, yp with total compensation force Fc and the point of its application xc, yc323
10.4. Designing the axial clearance compensation system in the machines of the third group325
10.5. Designing the axial clearance compensation system in the machines of the fourth group327
10.6. Conclusions331
11. Design solutions of fluid power gear machines333
References347

2.2.Idealandrealcharacteristicsofapumpandamotor

ancesGinthepump,formedbetweentherotatingdisplacementchamberTand

thefixedelementsofthehousing.Hence,Figure2.5adepictsthecharacteristicsofreal

deliveryQ

gdependingontheloadofthepump∆p

g,namelyQ

g±f(∆p

g).Thecharac-

teristicsresemblestheshapeofaparabola.BetweentheoreticalcharacteristicsQ

gtand

realcharacteristicsQ

g,volumetricloss∆Q

gismarked.Figure2.4bshowsthatthe

streamindicatingtheoreticaltorqueM

gtisincreasedbyhydraulic-mechanicalloss∆M

and,asaresult,theshaftofthepumphastobeloadedwithrealtorqueM

g.Hydraulic-

mechanicalloss∆M

gtorqueresultsbothfromtheresistanceoftheworkingfluidflow

throughthechannelsandtheclearancesinthepump,andthefrictionbetweenthose

partsofthepumpwhichremainintherelativemotionduringtheoperationof

thepump.Takingthatintoconsideration,Figure2.5bpresentsthecharacteristicofreal

torqueM

gdependingonpressure∆p

gworkingonthepump,namelyM

g±f(∆p

g).

CharacteristicM

gisstillastraightlinebutitisshiftedrelativetothecharacteris-

ticoftheoreticaltorqueM

gtbythevalueoftorqueloss∆M

TheanalysisofFigure2.5aallowstoobservethefollowingdependency:

g±Q

gt-∆Q

(2.6)

Thefigureshowsthatvolumetricloss∆Q

ggrowsproportionallytothegrowthof

pressure∆p

gworkingonthepump.Itresultsfromthetheoryofflowthrough

theclearances,whichstatesthattheflowthroughtheclearancesofthedisplacement

chamberandvolumetricloss∆Q

ggrowproportionallytothegrowthofthepressure

difference∆pinsideandoutsidethedisplacementchamber.

ByjuxtaposingrealdeliveryQ

gwiththeoreticaldeliveryQ

gt,thevolumetriceffi-

ciencyofthepumpcanbedefinedas:

(2.7)

TheanalysisofFigure2.5ballowstothedeterminethefollowingdependency:

g±M

gt+∆M

(2.8)

Thefigureshowsthatlosstorque∆M

ggrowsalongwiththegrowthofpressure

∆p

ginthepump.Thisoccursmainlyduetoanincreaseinthemechanicalfrictionand

anincreaseintheresistanceoftheworkingfluidflowinthechannelsofthepump.

ThecomparisonoftheoreticaltorqueM

gtwithrealtorqueM

genablesthedeter-

minationofthehydraulic-mechanicalefficiencyofthepump:

hmg

(2.9)

Consideringtherealpumpasamachinewhichcollectspowerfromthemotorand

transfersittothehydraulicsystem,itisnecessarytodeterminethepowerbalance.

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