Fundamentals of designing hydraulic gear machines Jarosław Stryczek

Spis treści książki

• Cover
• Title page
• Copyrights
• Spis treści
• Preface
• 1. Definition, systematics and methodology of designing hydraulic gear machines
  • 1.1. Definition and systematics
  • 1.2. Designing methodology
• 2. The process of energy transformation in hydraulic gear machines
  • 2.1. General models of a pump and a motor
    • 2.1.1. General model of a pump
    • 2.1.2. General model of a motor
  • 2.2. Ideal and real characteristics of a pump and a motor
    • 2.2.1. Characteristics of a pump
    • 2.2.2. Characteristics of a motor
  • 2.3. Conclusions
• 3. Gears in the hydraulic gear machines
  • 3.1. Teeth, gears and the external involute gear systems
    • 3.1.1. The tooth, the external gear
    • 3.1.2. The boundary number of teeth, correction of the external tooth
    • 3.1.3. The external involute gear system
      • 3.1.3.1. The uncorrected gear system, the principle of co-operation,the number of contact
      • 3.1.3.2. The corrected gear system, the principle of co-operation, the number of contact
  • 3.2. Teeth, gears and the internal involute gear systems
    • 3.2.1. The tooth, the internal gear
    • 3.2.2. The boundary number of teeth, the correction of the internal tooth
    • 3.2.3. The internal involute gear system
      • 3.2.3.1. The uncorrected gear system, the principle of co-operation,the number of contact
      • 3.2.3.2. The corrected gear system, the principle of co-operation, the number of contact
      • 3.2.3.3. Interference of the gear teeth
  • 3.3. Teeth, gears and the internal cycloidal gear systems
    • 3.3.1. Teeth, gears and the uncorrected internal epicycloidal gear system
    • 3.3.2. Teeth, gears and the corrected internal epicycloidal gear system
    • 3.3.3. Principle of co-operation in the epicycloidal gear system, the contact line, the number of contact.
    • 3.3.4. Teeth, gears and the uncorrected internal hypocycloidal gear system
    • 3.3.5. Teeth, gears and the corrected internal hypocycloidal gear system
    • 3.3.6. Principle of co-operation in the hypocycloidal gear system, the line of contact, the number of contact
    • 3.3.7. Principle of co-operation in the cycloidal gear system with moveable axes
    • 3.3.8. Principle of co-operation in the cycloidal multi-gear systems
  • 3.4. Conclusions
• 4. Channels and clearances in the fluid power gear machines
  • 4.1. The system of fixed channels and clearances
  • 4.2. The system of moveable channels and clearances
  • 4.3. The system of channels and clearances in the machines of the first group
    • 4.3.1. Inlet channel and inlet chamber
    • 4.3.2. Inlet bridge
    • 4.3.3. Outlet channel and outlet chamber
    • 4.3.4. Outlet bridge
    • 4.3.5. Axial and radial clearance
  • 4.4. The system of channels and clearances in the machines of the second group
    • 4.4.1. Inlet channel and inlet chamber
    • 4.4.2. Inlet bridge
    • 4.4.3. Outlet channel and outlet chamber
    • 4.4.4. Outlet bridge
    • 4.4.5. Axial and radial clearance
  • 4.5. The system of channels and clearances in the machines of the third group
    • 4.5.1. Inlet channel and inlet chamber
    • 4.5.2. Inlet bridge
    • 4.5.3. Outlet channel and outlet chamber
    • 4.5.4. Outlet bridge
    • 4.5.5. Axial and radial clearance
  • 4.6. The system of channels and clearances in the machines of the fourth group
    • 4.6.1. The system of channels and clearances in the multifunctional hydraulic gear machine (MHGM)
    • 4.6.2. The system of channels and clearances in the ORBIT orbital motor
    • 4.6.3. The system of channels and clearances in the MAX orbital motor with double cycloidal gearing
  • 4.7. Conclusions
• 5. Delivery and delivery pulsation, capacity and capacity pulsation of the fluid power gear machines
  • 5.1. General formulae
    • 5.1.1. Instantaneous delivery
    • 5.1.2. The proper, theoretical and average delivery
    • 5.1.3. Delivery pulsation
  • 5.2. Delivery and delivery pulsation in the machines of the first group
  • 5.3. Delivery and delivery pulsation in the machines of the second group
  • 5.4. Delivery and delivery pulsation in the machines of the third group
    • 5.4.1. Epicycloidal gear machines
    • 5.4.2. Hypocycloidal gear machines
  • 5.5. Delivery of the machines of the fourth group
  • 5.6. Conclusions
• 6. Pressure and pressure pulsation in the fluid power gear machines
  • 6.1. Theoretical characteristics of changes of the pressure and pressure pulsation in intertooth displacement chamber T in machines of the firstthird groups
  • 6.2. Theoretical characteristics of changes of the pressure and pressure pulsation in the intertooth displacement chamber in machines of the fourth group
  • 6.3. Conclusions
• 7. The visual study of the flow processes and phenomena in the channels and clearances of the gear machines
  • 7.1. General comments
  • 7.2. The subject and methodology of the visual study, the test stand
  • 7.3. The visual study of the machines of the first group
    • 7.3.1. Inlet channel and inlet chamber
  • 7.3.2. Inlet bridge
    • 7.3.3. Outlet channel and outlet chamber
    • 7.3.4 Outlet bridge
    • 7.3.5 Relief grooves in the outlet bridge zone
    • 7.3.6. Axial clearance
  • 7.4. The visual study of the machines of the second group
    • 7.4.1. Inlet channel and inlet chamber
    • 7.4.2. Inlet bridge
    • 7.4.3. Outlet channel and outlet chamber
    • 7.4.4. Outlet bridge
  • 7.5. The visual study of the machines of the third group
    • 7.5.1. Inlet channel and inlet chamber
    • 7.5.2. Inlet bridge
    • 7.5.3. Outlet channel and outlet chamber
    • 7.5.4. Outlet bridge
  • 7.6. Conclusions
• 8. Pressure study in the channels and clearances of the gear machines
  • 8.1. The subject and methodology of the study, the test stand
  • 8.2. Study of the pressure in the channels and clearances of the machines of the first group
    • 8.2.1. Study of gear pump I without the axial clearance compensation
    • 8.2.2. Study of gear pump II with the axial clearance compensation
  • 8.3. Study of the pressure in the channels and clearances of the machines of the second and third group
  • 8.4. Conclusions
• 9. Designing the housings of the fluid power gear machines
  • 9.1. Methodology of designing the housings of the fluid power gear machines
  • 9.2. Determining the design and technological requirements for the housings of the pumps
  • 9.3. Determining the basic shape of the pumps
  • 9.4. Strength analysis of the basic shape gear pump housings by means of FEM
    • 9.4.1. Geometrical models, load and fixation
    • 9.4.2. Numerical models, research programme
    • 9.4.3. Results of the strength analysis of the basic shape pump housings
  • 9.5. Global and local modification of the basic shape housing
  • 9.6. Strength analysis of the housings of the modified shape gear pumps by means of FEM
  • 9.7. Assumption of the final shape of the pumps
  • 9.8. Conclusions
• 10. Designing of the axial clearance compensation system
  • 10.1. Principle of axial clearance compensation. Methodology of designing the axial clearance compensation system
  • 10.2. Designing the axial clearance compensation system in the machines of the first group
    • 10.2.1. Assumption of a design solution of the compensation system
    • 10.2.2. Defining Ap area of the pressure working in the axial clearance, and the division of the area into partial areas Api
    • 10.2.3. Defining the distribution of partial pressure pi working on partial areas Api
    • 10.2.4. Defining partial pressure repulsive forces Fpi and pressure repulsive forces Fp
    • 10.2.5. Defining partial torques of the repulsive forces Mpi and total torque of the repulsive forces Mp
    • 10.2.6. Defining points of application xpi, ypi of partial pressure repulsive forces Fpi and point of application xp, yp of total pressure repulsive forces Fp
    • 10.2.7. Shaping total compensation area Ac and its division into partial areas Aci. Determining of compensation pressure pc
    • 10.2.8. Defining partial compensation forces Fci and total compensation force Fc
    • 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 Fc
    • 10.2.10. Comparison of total pressure repulsive forces Fp and its point of application xp, yp with total compensation force Fc and its point of application xc, yc.
  • 10.3. Designing the axial clearance compensation system in the machines of the second group
    • 10.3.1. Assumption of a design solution of the compensation system.
    • 10.3.2. Defining partial pressure repulsive forces Fpi and total pressure repulsive force Fp
    • 10.3.3. Defining points of application xpi, ypi of partial pressure repulsive forces Fpi and point of application xp, yp of total pressure repulsive force Fp
    • 10.3.4. Shaping total compensation area Ac and its division into partial areas Aci. Determining of compensation pressure pc
    • 10.3.5. Defining partial compensation forces Fci, coordinates xci, yci of the points of its application, total compensation force Fc and coordinates xc, yc of the point of its application
    • 10.3.6. Comparison of total pressure repulsive force Fp and its point of application xp, yp with total compensation force Fc and its point of application xc, yc
  • 10.4. Designing the axial clearance compensation system in the machines of the third group
  • 10.5. Designing the axial clearance compensation system in the machines of the fourth group
  • 10.6. Conclusions
• 11. Design solutions of fluid power gear machines
• About Author
• References

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