inline pumps by Cliff Speaks

A Descriptive Summary of Vickers Inline Pumps and their Applications

Vickers Fluid Systems

Index Inline Pump . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 Introduction . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3 Identification Code . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3 Features and Benefits . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3 Basic Operations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4 Drive Shaft and Bearings Bearing Size Minimized Self-Aligning Spline Cylinder Block No Support Bearing Needed Pistons and Shoes Precise Pressure Balance Low Cylinder Wear Yoke Shoe Bearing Plate Piston Shoe Hold-Down Plate Shoe Hold-Down Plate Retainer Valve Plate Decompression Phase Shaft Seal Rotating Sealing Element Spring Assures Contact External Sealing Materials General Application Advantages . . . . . . . . . . . . . . . . . . . . . . . . . . 8 Reliability Engineering Cooperation with Customers Performance Pressure Regulation Stability Temperature Range Efficiency Weight Economy Life Service Cost Reliability Flexibility of Installation Thru-Shaft Available Operational Characteristics . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 10 Life Normal Period of Operation Efficiency Effects of Inlet Pressure and Temperature Extremes Pressure Temperature Driving Speeds Transient Response The Speed at Which the Yoke Angle Is Changed Pump Driving Speed The Compliance of the Circuit The Nature of the Load The Use of an Accumulator Minimum Accumulator Size Desirable Inlet Pressurization Types of Controls . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 13 Standard Types Flat Cut-Off Type Differential Cut-off Type Electrically Depressurized Variable Pump with Blocking Valve Dual Range Control Constant Horsepower Control Provisions for Special Requirements Servo Control Intelligent Control TM Application Performance and Installation Data . . . 20 3000 psi (207 bar) 4,000 psi (276 bar) and Higher Performance Calculations Typical Performance Data and Installation Drawings . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23 Eaton Aerospace Worldwide . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 60

Inline Pump

Coupling Shaft Screw Shaft Seal Direction of Rotation Sleeve Coupling Shaft

Control Springs

Mounting Flange

Spring Guide Shoe Bearing Plate

Seepage Drain Port

Shoe Hold-Down Plate Hold-Down Plate Retainer

Yoke Pintle Bearing

Actuator Piston

Drive Shaft Bearing Rear Yoke Piston Shoe Piston

Sealing Screw

Drive Shaft Housing Drive Shaft Bearing Front Case Drain Port

Pilot Valve Spring Guide

Spring Retainer Cylinder Block Spring Cylinder Block Lift Limiting Washer

Compensator Spring Spring Seat

Retaining Ring Outlet Port

Valve Plate Inlet Port Compensator Adjusting Screw Lock Nut

Introduction

Features and Benefits

At Vickers Fluid Systems of Eaton Aerospace, we know how important it is to listen. And listening to our customers has shown us that quality, reliability and performance are the standards by which a company's products should be judged. Since 1921, Vickers has gained vast experience in the design and manufacture of hydraulic pumps. This is the heritage passed on to our aerospace inline pumps. Refinement of the basic inline pumping concept has brought the industry a truly superior series of high performance pumps. This bulletin is a technical description of the design and performance of the inline pump series. Also described is the variety of controls available. Intended as a convenient reference for the system designer, the bulletin provides the necessary information to predict unit performance and to select the proper type of control.

Low Cost Lower cost per horsepower than other pumps of comparable design.

Durable by Design Generous bearing surfaces and reduced contact pressures result in a more durable pump.

More Horsepower Lighter weight and higher speed capability provide a much higher horsepowerto-weight ratio.

Rapid Response Step changes from peak demands to minimal flow can be accomplished within 50 milliseconds.

Smooth Operation Low pressure pulsations minimize system disturbances and improve system life.

Economical Overhaul Overhauls are economical because of the minimum number of parts and the simplified rotating group.

Reliability Simplicity and conservative design parameters assure high reliability and the ability to tolerate off-design conditions.

Low Power Loss Compact rotating group and small antifriction bearing diameters result in minimum power loss.

Identification Code Vickers Inline Series Pumps are identified by model numbers that indicate the displacement and design release number. (see diagram below.)

IDENTIFICATION CODE

PV3-044-•• 2A xxx-xxx-•• xx Class 1 Changes in Sequential Order

Model Description Pump

A, B, etc.

Type of Displacement Fixed Variable

F V

1, 2, etc.

Product Group Inline

Release (Modifications of the Standard Model in Sequential Order) Source Code EA European (Delete for USA Source) Basic Frame Size Displacement in cu. in./rev. to the nearest hundredth (0.44 in 3/rev. shown)

Basic Operations Figure 1

Retainer Ring Cylinder Block Spring

Piston Shoe Housing Shoe Bearing Plate

Front Bearing

Piston

Drive Shaft Shaft Seal

Coupling Shaft

Rear Bearing

Valve Plate

Yoke Spring Assembly

Cylinder Block Yoke Actuator Piston Piston Shoe Hold-Down Plate

The Vickers inline pump series is a family of positive-displacement, axial-position pumps designed to operate at either fixed or variable displacement. Figure 1 is a cross-section of the typical inline pump. As the drive shaft rotates, it causes the positions to reciprocate within the cylinder block bores. The piston shoes are held against a bearing surface by compression force during the discharge stroke and by the shoe hold-down plate and retainer during the intake stroke. The bearing surface is held at an angle to the drive shaft axis of rotation by the yoke (Figure 2).

Intake Stroke

this intake stroke of the piston, fluid is supplied to its cylinder block bore through the valve plate inlet port.

Discharge Stroke Further rotation of the drive shaft causes the piston shoe to follow the shoe bearing plate toward the valve plate. This is the discharge stroke of the piston and fluid is expelled from its cylinder bore through the outlet port of the valve plate. Figure 3 illustrates the manner in which piston stroke is controlled by the yoke angle. Displacement variations that respond to pressure changes to vary the yoke angle are described on page 14.

As each piston shoe follows the shoe bearing plate away from the valve plate, the piston is withdrawn from the cylinder block. During

Figure 2

Figure 3

Maximum Pumping Angle

Valve Plate Yoke Cylinder Block Piston Drive Shaft

Drive Shaft Minimum Stroke Position Stroke

Drive Shaft and Bearings The drive shaft is a simple, single-piece design held in accurate alignment by two anti-friction bearings.

Bearing Size Minimized

mating surfaces are required to establish the proper geometric relationships of these components. The effective center of the cylinder block spline is located near the rotation plane of the piston shoes to minimize movement action on the cylinder block.

The shaft is supported by radial bearings at each end. Since radial loads (due to position forces on the cylinder block) are distributed between the two widely spaced shaft bearings (front and rear, Figure 1), bearing size is minimized, reducing friction losses. This is especially important in high-speed applications where the fluid disturbance and power loss in submerged bearings increases appreciably with bearing rpm and time.

Pistons and Shoes

Self-Aligning Spline

Precise pressure balance versus speed and load capability have been achieved without sacrificing efficiency and life. Thrust loads on the piston shoes are controlled by pressure balance to a point where the resultant loads can be adequately supported by the fluid film under their outer lands. (Figure 5).

The spline that drives the cylinder block is a major diameter fit, crowned slightly to provide cylinder block self-alignment.

Cylinder Block Optimum hydraulic pressure balance between the cylinder block and the valve plate (Figure 4), ensures proper hold-down, minimizes internal friction and reduces torque losses.

No Support Bearing Needed Radial loads resulting from piston reactions are carried to the drive shaft through the drive spline, eliminating the need for a support bearing on the cylinder block. Consequently, losses associated with such a large bearing are eliminated, in addition, this kind of load support provides optimum alignment conditions between the cylinder block, valve plate and drive shaft, since fewer

Stress analysis methods combined with verification tests have been used to arrive at an optimum piston-cylinder block design. The Vickers design places special emphasis on shoe design, since this is a critical link in the efficiency, life and reliability of the inline pump design.

Precise Pressure Balance

Low Cylinder Wear Since minimum piston engagement in the cylinder block bore is designed to be approximately two diameters, reaction forces between the pistons and cylinder block are minimized. This reduces bore wear so that internal leakage remains nearly constant with time.

tioned to allow optimum design of the actuating piston and control spring (Figure 6).

Shoe Bearing Plate The use of a shoe bearing plate allows simplified yoke design, accurate lapping of the bearing surface and optimum material selection.

Piston Shoe Hold-Down Plate During the inlet stroke, the piston/shoe subassembly requires force to pull it out of the cylinder block bore; this force is supplied by the hold-down plate. It is driven and guided by contact with the shoe necks, and is held in place axially by sliding contact with the hold-down plate retainer (Figure 7).

Shoe Hold-Down Plate Retainer The retainer provides positive retention of the shoe hold-down plate during the intake stroke. This retainer is secured to the yoke by screws to ensure optimum support of the shoe hold-down plate and minimum retainer loading in the areas where shoe lift forces (intake stroke) are highest. The retainer design and arrangement improve the highspeed capability of the pump.

; ;; ; ;; ;; ;;; ;; ; ; ;; ;;;; ;;; ;; Figure 4

Valve Plate

Yoke

Extensive studies have been performed on the yoke to provide a design with an optimum deflection-to-weight relationship. The yoke pivot centerline has been posi-

Figure 5

Figure 6

Valve plate kidney port slots have been designed to provide minimum power loss and pressure pulsation throughout delivery range. This is accomplished by designing the valve plate porting and yoke geometry Figure 7

Piston

Shoe HoldDown Plate

Hold-Down Plate Retainer

Piston

Cylinder Block

Piston

Shoe

Piston Circle

Pintle

Shoe Yoke Shoe Bearing Plate

so the piston chamber pressure is raised to system pressure before opening to the outlet port (precompression) and the piston chamber pressure is lowered to inlet pressure before opening to the inlet port (decompression).

Decompression Phase During the decompression phase, the energy stored in the unswept volume of fluid at system pressure is returned to the system by motoring, rather than being lost by throttling to inlet pressure.

Shaft Seal Vickers Aerospace Products has developed a shaft seal configuration especially designed for use in all aerospace pumps. Benefits of this design are longer life, greater reliability and lower overall pump costs. This face type shaft seal (Figure 8) is not a â&#x20AC;&#x153;packageâ&#x20AC;? design, but is a combination of simple elements. The elements most subject to wear can be repaired at overhaul and the sealing surface can be lapped, providing an inexpensive procedure for obtaining new seal performance.

Figure 8

Rotating Sealing Element The simplified seal is made of high quality material such as bearing grade bronze or carbon. The major difference from other seals is that the sealing element rotates with the shaft while the heavier mating ring is stationary in the housing. The seal assembly is driven by two tabs on the retainer that engage with the pump drive shaft. Static sealing around the circumference of the drive shaft is accomplished with the elastomeric grommet, shown in Figure 8, which is held in contact with the shaft by a garter spring. Dynamic sealing is effected by forcing the rotating element against the stationary mating ring. Constant force is provided by the wave washer; hydrostatic balance close to 100% assures that its operation is unaffected by a wide variation in case pressure.

Spring Assures Contact Since the elastomeric grommet is held in contact with both the shaft and the sealing element by means of mechanical springs, the effectiveness of the seal does not depend on the elastic properties of the grommet. Efficient sealing is not disturbed by the effects of either age or temperature. Also,

;;

because of the low mass of the elements mounted on the shaft, the seal maintains full contact, even in environments with high vibration levels.

External Sealing There are few external seals required in the standard design, and in newer designs none are subjected to high pressure. As a result, the pump has fewer potential external leakage paths. The structural integrity of the single piece housing has been proven by completing a 4-Life fatigue test (approx. 1,440,000 cycles). The design simplifies maintenance tasks, reduces pkg weight, and minimizes envelope requirements.

Materials Materials are chosen for high strength, long life and optimum performance. Materials used in the standard design include bronze, and steel for the rotating group and cast aluminum for the housing and mounting flange. The valve block may be steel, titanium or aluminum. High performance pumps generally use wrought or forged housing and mounting flanges.

Shaft Seal

Housing

Sealing Element

Mating Ring Elastomeric Grommet

Drive Shaft

Garter Spring

Spacer

Wave Washer

Retainer

General Application Advantages

The hydraulic pump that supplies power to move the various loads of modern aircraft and defense vehicles is a critical component. Determining the best pump for the job involves three basic considerations:

optimum performance in a Type II system as defined by MlL-H-5440G, -65° F to +275° F; (-54° C to 135° C) fluid temperature. Special modifications for operation at higher temperatures can be provided.

• Reliability

4) Efficiency

• Performance

Typical value of overall efficiency of Vickers inline pumps at rated operating conditions is 88%. Volumetric efficiency at rated operating conditions exceeds 96%. These efficiencies are maintained near these values for long operating durations.

• Economy

Reliability The safety of an airplane and its occupants, or the effectiveness of a missile, depends on the proper functioning of the hydraulic system. Realizing that product reliability is the most important factor to the consumer, Vickers sets this as the essential, guiding objective in all design, manufacturing and testing operations. This objective is further supported by the Product Support Department of Vickers Aerospace through field and overhaul work and statistical studies of pumps in use.

Engineering Cooperation with Customers Close and active engineering cooperation with the customer is aimed at providing the proper hydraulic circuit design necessary to obtain the most reliable pump performance. The wide use of Vickers pumps in all kinds of military and commercial aircraft and the record these pumps have established over the past years are evidence of the emphasis Vickers places on reliability.

Performance Certain standards and details of performance are required by hydraulic system designers. How well a pump meets or exceeds these specifications is obviously important. Vickers inline pump performance is defined in these five characteristics:

A pilot of performance versus time is shown in Figure 9.

Service Cost The uncomplicated design of the Vickers inline pump provides a unit that has low overhaul cost. The man-hours required for disassembly, maintenance operations, reassembly and retest are minimal. Parts costs are low and a minimum of inexpensive overhaul tools are needed.

Reliability

Vickers inline pumps have a high power-toweight ratio. For example, the PV3-115 pump has a ratio of 4.5 hydraulic output horsepower per pound (continuous rating), that rises to 5.4 hp/lb for overspeed operation.

The low wear rates, together with the added structural margin provided in the design, result in the ability of Vickers inline pumps to withstand frequent off design operating conditions of temperature, speed, pressure, etc., without noticeable damage or performance deterioration.

Economy

Flexibility of Installation

Economy involves original purchase price and operating costs. Operating costs in turn depend upon overhaul time, overhaul costs and reliability or unscheduled removal rate.

An additional consideration when choosing a hydraulic pump is flexibility of installation. Vickers inline pumps have standard mounting arrangements (QAD or bolt type) with a variety of inlet and outlet configurations available. The pressure control has been designed as an integral component, reducing space and weight. In addition, the pump design is ideally suited to manifold type inlet-outlet porting and the use of quick disconnect type mounting.

5) Weight

Life Vickers inline pumps have demonstrated long life capability both in qualification testing and in service. Nearly all models have completed the qualification requirements of MIL-P-19692. The longtime durability has been further demonstrated in a wide variety of applications and in other laboratory testing. One example is the extended endurance test of a PV3-115 pump, following qualification to MIL-P-19692. The pump was cycled between 10% and 90% flow at rated speed of 6000 rpm and at continuous Type II system temperatures. After 15,000 hours, the pump was still capable of meeting new pump performance requirements.

Thru-Shaft Available For systems where mounting pad availability is at a minimum, Vickers inline pumps can be provided with a thru-shaft and special end cap. This feature allows additional accessories to be mounted to and driven by the Vickers pump, reducing engine mounting pad requirements. Custom designing provides the package configuration that best fits a particular application.

1) Pressure Regulation

2) Stability Recovery from step loads and load pertubations is rapid, and pressure overshoots are not excessive when proper circuit design is employed.

3) Temperature Range Vickers inline pumps are designed to provide

Efficiency & Horsepower Versus Time

Figure 9 100

Volumetric Efficiency

Overall Efficiency

Horsepower Efficiency - Percent

System pressure is automatically held within a given range for all flows from zero to full flow. The regulation range may be chosen to best fit a particular requirement and may be as small as 3% of related pressure. The regulation compensates for changes in load demand, temperature and variation in driving speed.

Input Horsepower

60 50

Output Horsepower

Conditions Theoretical Displacement Temperature Fluid Speed Rated Pressure

30 20 10 0

2500

5000

7500

Time - Hours

1.15 cu. in./rev. 240°F (116°C) MIL-H-5606A 6000 rpm 3000 psi 10,000

12,500

15,000

Operational Characteristics

Life The life of a hydraulic pump depends to a great extent upon the operating temperature, the drive speed, and the pressure and flow extremes to which it is subjected. In addition, cleanliness of the hydraulic fluid and sufficient inlet pressure are very important for assuring long life.

Normal Period of Operation The normal period of pump operation between overhauls in aircraft application may range from 1000 to more than 15,000 hours of actual pump running time. For applications involving operation at fluid temperatures above 275° F (135° C), the overhaul period may be shorter.

Efficiency Overhaul efficiency varies somewhat with drive speed and outlet pressure. This value usually exceeds 85% and may be more than 90% at rated pressure and moderate speeds. During idle, the pump provides only enough flow to satisfy its own internal leakage. In the case of the EDV pump, in which leakage is circulated at low pressure instead of rated pressure during idle periods, the power loss is further reduced.

Effects of Inlet Pressure and Temperature Extremes Inlet pressure will adversely affect efficiency when it drops below the critical inlet pressure and causes cavitation. Extremes of temperature also will somewhat reduce efficiency. At high temperatures the fluid viscosity is lowered and leakage increases. Low temperature increases fluid viscosity and increases windage loss. However, the oil quickly warms up as the pump operates. The effect of temperature is minimal except at very high or very low extremes.

Pressure Most Vickers pressure-compensated pumps are designed for 3000 psi (207 bar) maximum outlet pressure at zero flow and automatically limit the steady state pressure to this value. During transient periods, pressure surges may instantaneously exceed this by about one-third or less. Full flow maximum pressures are usually 2900 psi (200 bar). Higher pressure pumps, especially 4000

Speeds of Vickers 3,000, 4,000 and 5,000 psi Variable Displacement Pumps Pump Size PV3-003 PV3-006 PV3-008 PV3-011 PV3-019 PV3-022 PV3-032 PV3-044 PV3-049 PV3-056 PV3-075 PV3-115 PV3-150 PV3-205 PV3-240 PV3-300 PV3-375 PV3-400 PV3-488

Normal 18,000 15,000 13,500 12,500 12,100 10,000 9,000 8,000 8,800 8,200 7,000 6,600 6,000 5,900 5,300 5,000 4,800 4,400 4,100

Recommended Speed (rpm) Maximum 22,500 18,750 16,800 15,600 15,100 12,500 11,250 10,000 11,000 10,250 8,750 8,250 7,500 7,400 6,600 6,250 6,000 5,500 5,125

The above speeds depend upon the application, life required, duty cycle, temperature and other factors that should be evaluated by Vickers engineers for a given application.

psi, 5000 psi and 8000 psi (276 bar, 345 bar and 552 bar) are being used in an increasing number of applications which are at the forefront of hydraulic technology. Dual range pumps provide two separate pressure ranges. (See Controls section, page 14, for description of compensators).

Temperature Temperature limits for Type II systems per MIL-H-5440G continuous full-life operation are -65° F to +275° F; (-54° C to 135° C). Vickers standard inline units can be operated within these limits.

Driving Speeds The driving speed recommended for a particular size pump is based on pump life considerations. The maximum speed values shown represent an optimum compromise between long pump life (lower speeds) and maximum power output (higher speeds) and may be exceeded under certain conditions.

Transient Response When a sudden load change causes system pressure to exceed the lowest value of the pump's pressure regulation range, or when a sudden load change occurs while system pressure is in the regulation range, the pump must rapidly adjust the output flow to meet the new load condition. This requires that the yoke be repositioned rapidly. The time elapsed during the pressure change is a measure of the dynamic response of the pump and its associated circuit and load, and depends upon the following factors:

1) The Speed at Which the Yoke Angle is Changed This is a characteristic of the pump. For example, small yoke cylinder area and high control value gain contribute toward rapid yoke motion for both increasing and decreasing displacements.

2) Pump Driving Speed Pump speed affects time response because the rate of flow is proportional not only to yoke angle, but also to pump driving speed. When pump speed is high, the output flow will be high and pressure build-up time will be short.

3) The Compliance of the Circuit Circuit compliance is determined by the volume of oil under compression, the bulk modulus of the oil (varies with temperature and kind of fluid), elasticity of the lines and whether an accumulator is used. Small oil volume, high-bulk modulus, low-expansion lines and absence of an accumulator con-

tribute to fast pump response. A given flow change will result in a rapid pressure change, causing the pump to regulate rapidly.

4) The Nature of the Load The nature of the load influences how rapidly a change in load resistance or flow-control is reflected in a change in system pressure. Since changes in system pressure cause the pump to regulate, the nature of the load is a factor in the speed of pump response. In general, if the load has a high resonant frequency (low inertia, high spring rate, low damping), response of the pump to changes in load resistance or flow control valve settings will be faster than in the case of a low-frequency load system.

5) The Use of an Accumulator Although the use of an accumulator decreases the speed of pump yoke response, the speed of load response is the important factor. With an accumulator in the system, flow will be supplied rapidly to the load when needed, thereby contributing to fast load response. Although the pump yoke repositions more slowly because of the accumulator, the load does not sense the reduced yoke response since the pump's function is temporarily taken over by the accumulator.

Minimum Accumulator Size Desirable In order to keep the accumulator size at a minimum, the pump response should be as fast as possible. The size of the accumulator determines the time during which it can supply a given flow at a steady pressure. If a pump requires a relatively short time

3000 psi (207 bar) Inline Pump Series

to adjust flow to a new rate, a small accumulator may be used or the accumulator may be eliminated.

Inlet Pressurization When a pump is driven at high speed with insufficient pressure, cavitation may result due to the vacuum created during the intake stroke, and its sudden collapse. Also, when flow demand is suddenly increased, the inertia of the fluid in the inlet line can reduce the pressure at the pump inlet below the critical value and produce cavitation and water hammer. This has the tendency to tear particles of metal from the affected surfaces with resulting erosion. The amount of inlet pressurization required to prevent cavitation increases with the pump operating speed, as shown in the chart on page 59. The chart shows recommended inlet pressure for long life when operated in MIL-H-5606 or MIL-H-83282 fluid. For operation with phosphate ester based fluids, inlet pressures higher than those shown are recommended. Short time operation below the recommended values can be accommodated. Inlet pressure limitations of specific installations should be discussed with the Vickers application engineer. Vickers pumps can be supplied with various control arrangements, each particularly advantageous for certain individual application requirements. The pressure regulation characteristics of a pump are determined by the type of control employed.

Types of Controls

Standard Types The standard control types are the “flat cutoff” and “differential cut-off” compensators.

Flat Cut-Off Type This control provides nearly constant pressure through the entire flow range (Figure 10) by limiting the system pressure increase to about 3% from full flow to zero flow. It has the advantages of nearly constant output pressure, high power output, minimum size and weight and fast response.

Description A step-by-step description will give a better understanding of what happens in the control circuit of the flat cut-off type pump. For simplicity, an ideal pump is described (one that maintains a constant load pressure for all values of flow within the capacity of the pump, except when there is insufficient load to build up the pressure). Actually, as mentioned above, pressure rises about 3% as flow decreases from maximum to zero; this is caused by leakage from the control circuit and is important for pump stability. Refer to Figure 11. Assume that initially there is no resistance to flow. This will give zero system pressure and maximum flow (yoke to maximum angle).

Increasing Load As the load (resistance to flow) is increased, the pressure rises and flow remains maximum until the pressure reaches the pressure setting of the compensator valve spring. (A pressure setting or rated pressure of 3000 psi (207 bar) is assumed here; however the same description of operation also applies to pumps of higher rated pressures.) Therefore,

Flow Proportional to Compensator Valve Opening

Internal Leakage

Flow - % of max.

100%

As further load increase causes the system pressure to exceed 3000 psi (207 bar), the compensator valve spool is moved downward (as shown in Figure 11) and flow from the Ps line is metered to the yoke actuating piston. This flow increases with compensator valve opening and therefore with system pressure increase above 3000 psi (207 bar).

Pump Leakage Flow Maintained

Control Flow Integrated

In the preceding explanation, it was assumed that the pump has ideal regulation; that is, no increase in supply pressure as flow decreased from maximum to zero. As stated, this is not obtainable in practice because of leakage. Any leakage out of the control circuit requires an opening of the compensator valve to replace the leakage and maintain yoke position. An increase in supply pressure is required to produce the compensator valve displacement. Also, since a smaller yoke angle requires higher control pressure (compression of the yoke spring is greater), the leakage increases which, in turn, requires a greater compensator valve displacement and, therefore, a greater increase in supply pressure. A certain amount of control circuit leakage is desirable, since it limits the gain and helps to assure stable operation.

The yoke actuating piston integrates the control flow; thus, the velocity of the piston (and yoke) is approximately proportional to the position of the compensator valve. The rate of system flow reduction varies with pressure above compensator pressure setting. The yoke angle is reduced until the flow is just sufficient to give the set system pressure. At this point the yoke is in its new position and the compensator valve spool is centered.

Decreased Load If the load is decreased, the system pressure is temporarily reduced and the compensator valve spool will be displaced upward, opening the yoke actuating piston to case pressure.

If the main line flow is completely blocked, the yoke will be moved to near center, with only enough displacement to provide the pump leakage flow. The system pressure will be maintained and the pump will provide flow when required.

Ideal Cause Was Assumed

Figure 11

Compensator Valve

Pcase Case Drain

Pump Yoke

Ps High Pressure

Compensator Valve Spring 0

System Pressure (% of rated)

100%

Drive Shaft

Inlet Pi Low Pressure Pressure Adjustment ■ (Pi) Inlet Pressure

The yoke actuating spring will cause the yoke angle to increase until the flow is just sufficient to again give the set system pressure. The yoke is in its new position and the compensator valve spool is centered.

Outlet

Figure 10

3000 psi (207 bar) system pressure is just sufficient to center the compensator valve spool.

Control Pressure (Pc) Yoke Spring Yoke Actuating Piston

■ (Ps) Outlet Pressure ■ (Pc) Control Pressure

■ (Pcase) Case Pressure

Factors Influencing Regulation Other design constants influence the regulation, but leakage is the reason that any regulation range exists. Factors tending to make the static regulation curve more vertical (higher gain) include low spring rates (compensator valve and yoke), low leakage, large areas (compensator valve and yoke actuating piston) and high yoke centering force.

Differential Cut-Off Type This type of control provides a somewhat greater proportional decrease in pressure as flow increases from zero to maximum (Figure 13). A typical pressure regulation range is 20% of rated pressure, e.g. 600 psi (41 bar) for a 3000 psi (207 bar) setting. Advantages include proper load division in systems employing two or more pumps in parallel, minimum transient pressure surges and a high degree of stability.

Description The following step-by-step description explains how the differential type pump operates to automatically limit system pressure and to provide a proportional decrease in system pressure from the maximum to a given pressure, as flow increases from zero to maximum. The regulation range assumed

is 2400 to 3000 psi (165 to 207 bar). The range can be altered to obtain optimum characteristics for a particular application.

System Pressure Less Than 2400 psi (165 bar) Refer to Figure 12. The compensator valve spool will remain displaced upward at system pressure Ps less than 2400 psi (165 bar) due to the preload of the compensator valve spring. With the compensator valve spool displaced upward, the yoke actuating piston is ported to case. Therefore, the yoke actuating spring holds the yoke at the maximum angle (maximum flow position).

System Pressure More Than 2400 psi (165 bar) As system pressure (Ps) exceeds 2400 psi (165 bar) (due to increase in load), the upper metering orifice of the compensator valve opens and the bottom orifice closes. Flow from the control pressure (Pc) line enters the yoke actuating piston, compressing the yoke spring and decreasing the yoke angle. As the spring is compressed, the control pressure, Pc, rises. When the increase of Pc equals the amount by which Ps exceeds 2400 psi (165 bar), the valve will be centered to keep the yoke in its new position.

Pcase Case Drain

The yoke position is proportional to yoke spring compression and to the increase in Pc above case pressure. Therefore, reduction of yoke angle and flow are proportional to the increase in Ps above 2400 psi (165 bar).

Increasing System Pressure Flow is reduced from maximum to zero as system pressure increases from 2400 to 3000 psi (165 to 207 bar). Therefore, when Ps is 2600 psi (179 bar), a rise of 200 psi (14 bar), the flow is reduced by one-third. When Ps is 2800 psi (193 bar), a rise of 400 psi (28 bar), flow is reduced by two-thirds.

Decreasing System Pressure

Figure 12

Compensator Valve

Flow Reduction Proportional to Ps above 2400 psi (165 bar)

Pump Yoke

Outlet

When Ps is between 2400 and 3000 psi (165 to 207 bar), any decrease in Ps causes the compensator valve spool to be displaced upward and oil in the yoke actuating piston is ported to case, until Pc decreases enough to allow the spool to return to the centered position again. At this point the yoke remains in its increased-flow position. Therefore, the proportional relationship applies also to increase of flow with respect to decrease of pressure.

Summary In summary, pump output flow is inversely proportional to system pressure excess above 2400 psi (165 bar), as the pressure varies within the regulation range 2400 to 3000 psi (165 to 207 bar). Flow is maximum for 2400 psi (165 bar) and less. Flow is zero for 3000 psi (207 bar), except for internal leakage flow to supply lubrication. System pressure cannot exceed 3000 psi (207 bar) (except for small transient surges during sudden load changes) and the pump will rapidly provide flow when required.

Ps High Pressure

Figure 13 20%

Compensator Valve Spring Inlet Low Pressure

Drive Shaft

Pressure Adjustment ■ (Pi) Inlet Pressure

Control Pressure (Pc) Yoke Actuating Piston

■ (Ps) Outlet Pressure ■ (Pc) Control Pressure

Flow - % of max.

100%

Yoke Spring

Leakage

System Pressure (% of rated)

100%

■ (Pcase) Case Pressure

Figure 14

Pcase Case Drain

Depressurizing Piston

Blocking Valve

Pump Yoke

Outlet

Ps High Pressure

Drive Shaft

Yoke Spring

Inlet Pi Low Pressure EDV Solenoid (De-energized) ■ (Pi) Inlet Pressure

Compensator Valve

■ (Ps) Outlet Pressure ■ (Pc) Control Pressure

Electrically Depressurized Variable Pump with Blocking Valve This control further reduces the power loss when the pump is on standby by reducing system pressure to a lower value – example, 600 to 1000 psi (41 to 69 bar) by means of an electrical signal.

Description The solenoid valve (Figure 14) is normally de-energized. In this position the pump pressure compensator operates normally to provide full outlet pressure. The blocking valve is maintained in the open position (as shown) for outlet pressure above e.g. 400 psi (28 bar). Energizing the solenoid will port outlet pressure to a depressurizing piston that moves the compensator valve spool down.

Control Yoke Actuating Piston Pressure (Pc) ■ (Pcase) Case Pressure

This connects pump outlet pressure directly to the yoke actuating piston. Since the control pressure required to hold the yoke in zero stroke position is only that necessary to overcome the yoke springs, e.g.1000 psi (69 bar) for a 3000 psi (207 bar) pump, the pump is depressurized to a 1000 psi (69 bar) level. This results in a lower input torque to the unit and a lower power loss. High pressure is also ported to the spring chamber of the blocking valve when the solenoid is energized. This hydraulically balances the blocking valve piston and allows the spring to move the piston down to the closed position. The pump is thereby isolated from the system. The EDV/blocking valve feature has three primary uses: 1) It enables individual pumps to be taken off the line during system checkout and facilitates troubleshooting system malfunctions. 2) It enables a disabled system to be shut down in flight to avoid additional system damage or to prevent loss of system fluid.

■ EDV Pressure

3) If the pump is depressurized during an engine start, the peak torque of the pump during startup is reduced. This is particularly important if the pump is to be driven by an auxiliary power unit or air turbine. It may be impossible to start the power unit or air turbine unless this feature (or a flow bypass) is incorporated.

EDV Used with Either Type Cut-Off Although Figure 14 shows a flat cut-off compensator, the EDV feature also may be used with the differential type. It has no effect on the pump's regulation characteristics except when the solenoid is energized. Since the driving speed of the pump is continuous and unaffected by depressurization, the outlet pressure builds up very rapidly when the solenoid circuit is opened.

Figure 15

Compensator Valve

Case Drain

Pcase

Outlet

Pump Yoke

Ps High Pressure

Drive Shaft

Stop for High Pressure Range Stop for Low Pressure Range Compensator Valve Spring Inlet

Yoke Spring

Pi Low Pressure

■ (Pi) Inlet Pressure

Pilot Pressure

Yoke Actuating Piston

■ (Ps) Outlet Pressure ■ (Pc) Control Pressure

■ (Pcase) Case Pressure

EDV Feature without Blocking Valve

Preload Determines System Pressure

If the hydraulic system contains a check valve close to the pump outlet port and normal system pressure is maintained during periods of pump depressurization, the blocking valve may be eliminated. This results in savings of cost, envelope and weight.

As previously explained, the preload on the pressure compensator spring determines the system pressure at which the pump begins regulating. Compressing the spring (increasing preload) causes the pump to regulate at a higher pressure, and conversely, relaxing the spring (decreasing preload) provides regulation at a lower pressure.

Dual Range Control This control provides two separate output pressure ranges (Figure 16). Selection is made by means of an external signal (electrical, mechanical or hydraulic). It permits the use of smaller hydraulic components in systems that require short, high-power demand periods. The dual range control also reduces friction and leakage losses during low-power demand periods. Extended pump life is still another benefit.

No Pressure at “E” As seen in Figure 15, the compensator spring is in the extended position (low preload) when there is no pilot pressure at “E”. This means that a relatively low system pressure is required to overcome the spring preload force and the pump will regulate at its lower range.

Figure 16 100%

Upper Range

Flow - % of max.

E Two Position Compensating Piston

Lower Range 0

System Pressure (% of rated)

100%

Pressure at “E” When pilot pressure acts at “E”, the lower end of the spring is forced upward until a stop is reached. The position of this stop determines the amount of additional spring preload and thus determines the system pressure at which regulation in the higher range occurs. The pressure at “E” must be sufficient to hold the piston firmly against the stop. This pressure can be provided from an external source, or it can be supplied from the pump output through a solenoid-controlled valve. 17

Constant Horsepower Control This control limits power output to a given value for a given pump speed and maintains it at a nearly constant level within a given flow range (Figure 18). It has the advantage of keeping pump power source requirements at a minimum. The purpose of the constant horsepower is to limit the maximum pump power by beginning flow reduction at a given intermediate system pressure (point A) and to cause the pump to reach near rated pressure at a given intermediate flow (point B).

Yoke Spring Preloaded Refer to Figure 17, System pressure, Ps acts at all times on area “H”. The yoke spring is preloaded with a force equal to area “H” multiplied by the pressure at which it is desired to have flow reduction begin (refer to point A in Figure 18). As system pressure reaches this value, the preload is overcome and further pressure increase will produce a proportional decrease in flow. The rate of the spring and the area “H” will determine the slope from “A” to “B” (Figure 18)

Design Flexibility Allowed

2) Startup Bypass Valve

This control allows considerable design flexibility. As system pressure reaches a value slightly less than rated, the compensator valve opens, control pressure acts on area “C”, and from point B to zero flow, the pump operates as a basic flat or differential cut-off unit.

A simple, reliable, low-cost valve may be incorporated in the pump valve block to bypass flow and minimize torque during startup. This is sometimes important to reduce cranking torque of an engine or startup current of a motorpump. The flow is bypassed to inlet, at very low pressure, until a given flow is reached; the bypass valve then closes and remains closed until system pressure is reduced to near zero, at which time it opens and is ready for the next start. Operation is completely automatic and selfcontained. There are no electrical connections and torque during startup is even less than that of the EDV feature in the depressurized mode.

Provisions For Special Requirements 1) Integral Boost Stage If your application requires the pump to operate at unusually low inlet pressure, a boost stage can be added. This is a centrifugal pump that permits operation at inlet pressure well below atmospheric. A typical application is an aircraft main engine pump with a minimum inlet requirement of five psia. The impeller adds to the length and weight of the pump, but results in overall system weight reduction and increased reliability in applications where inlet pressure may be quite low.

3) Pressure Pulsation A pulsation damping chamber (attenuator) can be incorporated in the valve block to provide reduction of the outlet pressure ripple. This adds to the envelope and weight of the pump, but is justified for applications where lower pressure pulsation levels are essential and the required compressibility is not provided by the load circuit.

Figure 17

Pcase Compensator Valve

Case Drain

Outlet Ps High Pressure

Pump Yoke Drive Shaft

Compensator Valve Spring Yoke Spring

Inlet Pi Low Pressure Pc Pressure Adjustment ■ (Pi) Inlet Pressure

Area “C”

Area “H” (annular area) Yoke Actuating Piston

■ (Ps) Outlet Pressure ■ (Pc) Control Pressure

■ (Pcase) Case Pressure

Servo Control

Intelligent Control

Servo Control of variable displacement pumps is defined as a control where the output is proportional to the input signal. The output may be pressure or flow. The control valve usually is an electrohydraulic valve but could be direct drive, fluid, pneumatic or other type valve. There are two methods of servo signal control for variable pumps and motors. The first is used where only a variable pressure setting is desired. This provides a variable delivery component with a variable pressure setting determined by the control signal. The second method of servo control is to vary the displacement of the pump to provide flow proportional to the control signal. This type of control is generally used with a feedback network to control velocity or position of an actuator, or speed of a rotating device like a constant speed generator.

Intelligent Control is a trademark for a Vickers controller that can be used with variable pumps or motors. This controller can furnish all the characteristics of the controls mentioned in this brochure plus additional control capability such as position control. In addition, the Intelligent Control has more accuracy and flexibility. One control function can be commanded with a single control module. In addition to various control functions, Vickers Intelligent Control has the capability to provide diagnostics, built in test, health monitoring and integrity testing. The pressure and power control mode characteristics in Figure 19 show the precise control that is available with the Intelligent Control. The control can also be programmed to limit transient cavitation, reduce starting torque requirements and control multiple components. The Intelligent Control has been designed to be central to a hydraulic energy management system that will minimize system heat rejection and reduce the total system weight.

Figure 19

Figure 18

100%

(Actual constant horsepower curve, QP = K, is a hyperbola that is closely approximated by the line AB)

Rated Pressure

100%

4000 rpm

3200 rpm

2500 rpm

20 10 0

System Pressure (% of rated)

Flow - gpm

Flow - % of max.

}

Region of Constant Horsepower

1000

2000

3000

Pressure (psi)

Application Performance and Installation Data

3000 psi (207 bar) 3000 psi (207 bar) has been the most commonly used system pressure for aerospace applications. Vickers has created variable displacement pumps to meet the full range of 3000 psi (207 bar) power applications. Virtually all Vickers pumps have been qualified and sufficient testing has been performed to generate the typical performance curves shown in this section. The table to the right presents the basic characteristics for Vickers 3000 psi (207 bar) pumps.

4000 psi (276 bar) and Higher Higher system pressures have been selected for military applications and have been in use for several years. These applications normally require additional Vickers engineering involvement.

Basic Model Characteristics of 3000, 4000 and 5000 psi Pumps Basic Model No. PV3-003 PV3-006 PV3-008 PV3-011 PV3-019 PV3-022 PV3-032 PV3-044 PV3-049 PV3-056 PV3-075 PV3-115 PV3-150 PV3-205 PV3-240 PV3-300 PV3-375 PV3-400 PV3-488

Maximum Maximum Displacement Displacement in3/rev. mL/rev. 0.030 0.5 0.061 1.0 0.08 1.31 0.11 1.803 0.192 3.15 0.22 3.605 0.32 5.244 0.44 7.210 0.488 8.0 0.56 9.177 0.75 12.29 1.15 18.85 1.50 24.58 1.80 29.50 2.40 39.33 3.00 49.16 3.75 61.45 4.0 65.55 4.9

80.30

TypicalSpeed Speed Typical (rpm) (rpm) Normal Max.Ov.Sp. 18,000 22,500 15,000 18,750 13,500 16,800 12,500 15,600 12,100 15,100 10,000 12,500 9,000 11,250 8,000 10,000 8,800 11,000 8,200 10,250 7,000 8,750 6,600 8,250 6,000 7,500 5,900 7,400 5,300 6,600 5,000 6,250 4,800 6,000 4,400 5,500 4,100

5,125

Theo.Flow Flowatat Theo. NormalSpeed Speed Normal gpm L/min. 2.38 9.00 3.96 15.00 4.68 17.72 5.95 22.53 10.07 38.12 9.52 36.05 12.47 47.19 15.24 57.68 18.60 70.40 19.88 75.25 22.73 86.03 32.86 124.4 38.96 147.5 45.97 174.0 55.06 208.4 64.94 245.8 77.92 295.0 76.19 288.4

lbs. 1.7 2.4 3.4 3.7 3.7 4.6 6.0 7.1 6.4 7.1 8.9 11.5 15.0 19.8 22.5 28.0 34.5 33.5

kg. 0.8 1.1 1.6 1.8 1.7 2.1 2.7 3.2 2.9 3.2 4.0 5.2 6.8 9.0 10.2 12.7 15.6 15.3

86.97

46.3

21.0

329.2

DryWeight Weight Dry

Metric Units

American Standard 1) Flow

Q = in3/rev. x rpm 231

(gpm)

1) Flow

Q =

mL/rev. x rpm 1000

(L/min)

2) Torque

T = in3/rev. x psid 2π

(lb-in)

2) Torque

T =

mL/rev. x bar * 20π

(N•m)

3) Power (Shaft)

hp = Torque x rpm 63,025

(hp)

3) Power (Shaft)

W = π x Torque x rpm 30

3a) Power (hydraulic) hp =

gpm x psid 1714

(hp)

(watt)

3a) Power (hydraulic) W = 5/3 x L/min. x bar * (watt) KW = L/sec. x MN/m2 (kilowatt) * KPa/100 or 10 MN/m2 may be used in place of bar

Note: The above equations give theoretical values: that is, 100% efficiency is assumed. Actual pump outlet flow is less by the amount of pump internal leakage, and input torque to the pump is greater by the amount of torque loss.

Performance Calculations

FOR EXAMPLE for a PV3-075 pump, using typical efficiencies:

The following efficiencies are given as a guide for obtaining preliminary flow, torque and power performance values for rated speed and pressure. Since flow and torque losses also vary with fluid temperature, type of fluid and other operating conditions, we recommend that a Vickers application engineer be consulted before finalizing the design parameters. This is especially true if outlet pressure or pump driving speed for the application is different from rated pressure (3000 psi) and normal speeds listed on pages 11 and 21. The curves on pages 24 through 56 give performance values for most of the models at three different speeds. Typical performance through the pressure and flow range at 2/3 rated speed, full rated speed and 125% rated speed are shown (except for PV3-300 and PV3-375 for which the curves are at somewhat higher speeds). A generalized curve of recommended inlet pressures for various pump speeds is included on page 59.

Pump Efficiencies at Normal Recommended Speeds. 3000, 4000 and 5000 psi Pressures. 5000 psi 4000 psi 3000 psi

Efficiency Volumetric Torque Overall Typical (average) Minimum Typical (average) Minimum Typical (average) Minimum

0.96

0.92

0.885

0.94

0.905 0.85

0.95

0.94

0.93

0.925 0.86

0.94

0.95

0.92

0.935 0.86

0.89

Flow To obtain the value of pump outlet flow, calculate the theoretical value using pump equation number 1) from page 21, and MULTIPLY that flow by the applicable volumetric efficiency. Subtract outlet flow from theoretical flow to obtain flow loss. Qtheo = (.75 cu in/rev) (7000) rpm) = 22.7 gpm 231 Qoutlet = (22.7 gpm) (.96) = 21.8 gpm Qloss = (22.7 - 21.8) = 0.9 gpm (Multiplying by .96 Volumetric Efficiency)

Torque To obtain the value of pump input torque, calculate the theoretical value using pump equation number 2) from page 21, DIVIDE that torque efficiency. Subtract theoretical torque from input torque to obtain torque loss. Ttheo = (.75 cu in/rev) (3000 psid) = 358 lb•in 2π Tinput = 358 lb•in = 389 lb•in .92 Tloss = 389 - 358 = 31 lb•in (Dividing by .92 Torque Efficiency)

Shaft Input Power Shaft input power is calculated by multiplying input torque (obtained above) by shaft speed, and dividing by 63,025 (see pump equation number 3 from page 21). HPinput = (389 lb•in) (7000 rpm) = 43.2 HP 63,025 (389 ib•in is Tinput calculated above)

Hydraulic Output Power Hydraulic output power is calculated by multiplying outlet flow (obtained above) by differential pressure, and dividing by 1714 (see pump equation 3a from page 21). HPoutput = (21.8 gpm) (3000 psid) = 38.2 HP 1714 (21.8 gpm is Qoutlet calculated above)

Power Loss Power loss is obtained by subtracting the value of hydraulic output power form shaft input power. Power loss can also be obtained by using either of the following equations: Power Loss = (Power Input) (1 - overall efficiency) 1 Power Loss = (Power Output) ( -1) overall efficiency HPloss = 43.2 - 38.2 = 5.0 HP (also, HPloss = (43.2) (1 - .885) = 5.0 HP) 1 (and, HPloss = (38.2) ( - 1) = 5.9 HP .885

Typical Performance Data and Installation Drawings

2800

2900

3000

2800

2 Delivery - gpm

Delivery - gpm

3 4

Horsepower Loss

e r orqu owe Input T sep r o er tH pow Inpu orse H t pu Out

Outlet Pressure

iency Overall Effic

13,500 rpm

100

3100

2900

2 Horsepower Loss

er pow orse ut H p t u O

Inpu

owe

rsep

t Ho

ue orq ut T Inp

3000

Efficiency - Percent

Outlet Pressure ncy Efficie verall

Horsepower Horsepower

100

( P) Outlet Pressure - psi

Input Torque - lb. ins. Input Torque - lb. ins.

3100

2800

800

1200 1600 2000 ( P) Outlet Pressure - psi

2400

4 3 Delivery - gpm

5 2

10 Horsepower Loss

10 4 20

0 3200

r owe rsep t Ho Inpu er pow orse ut H Outp

Outlet Pressure ency Overall Effici ue orq ut T Inp

16,800 rpm

2800

2900

100

3000

Outlet Flow 3100

400

0 0

0.5

Horsepower Loss

2 1.5

que t Tor

r owe sep Hor

Inpu

pu Out

t Ho Inpu

owe rsep

Outlet Flow

Volumetric Efficiency

ency iciien Effic Overall Eff

13,500 rpm

2.5

3.5

100

5 4.5

( P) Outlet Pressure - psi

Horsepower Horsepower

9000 rpm

Efficiency - Percent

Input Torque - lb. ins. Input Torque - lb. ins.

24 Efficiency - Percent

PV3-008

PV3-008 inches (mm)

2800

3000

2900

100

3100

3 Delivery - gpm

12,500 rpm

2 Delivery - gpm

e Torqu

Horsepower Loss Horsepower Loss

r ppoowwere Horsee InInppuuttH powwerer epo utt HHoorrsse utpu OuOtp

Input

Outle Outlett Press Pressuure re

Overall Efficiency

Horsepower Loss

Output H

orsepow

sepower

Input Hor

e Torqu Input

Overall Efficien

Outlet Pressure

2900

100

3000

8000 rpm

Horsepower Horsepower 0

100

2800

2900

0 4 Delivery - gpm

0 0

2 6

Horsepower Loss Horsepower Loss

20 4 10

100

r owwere rseeppo rs utt HHo u tp e p u t e u rqu OuO t Toorq InInppuut

InInppu

r owwere rseeppo tHHo

Outle Outlett Pres Presssure ure Overall Overall Efficiency Efficiency Efficiency

15,600 rpm

1200 1600 2000 ( P) Outlet Pressure - psi

800

100

400

Horsepower Horsepower Loss Loss 0 2400 2800 3200

Delivery Delivery Deliver

poowwerer Horseep InInppuuttH powwerer epo utt HHoorrsse utpu OuOtp

e TToorqrquue InInppuutt

cy cienncy Effiicie erarallll Eff OvOve

Volumetric Volumetric Efficiency Efficiency

100

3000

3100

18 16

100

12,500 rpm

PV3-011P

Horsepower Horsepower

3100

Efficiency - Percent

Input Torque - lb. ins. Input Torque - lb. ins.

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

Efficiency - Percent Efficiency - Percent

Input Torque - lb. ins. Input Torque - lb. ins.

V3-011

PV3-011P

V3-011 inches (mm)

3000

3100

4 Delivery - gpm

Delivery - gpm

10 Horsepower Loss

3000

100

3100

1500

2000

3500

8 Delivery - gpm

3000

e Torqu Input

Overall Efficiency

Outlet Pressure

2500

Horsepower Loss

er epow t Hors Inpu wer rsepo ut Ho Outp

15,100 rpm

( P) Outlet Pressure - psi

1000

wer

500

rsepo

ut Ho

Horsepower Loss

Outp

er epow Hors Input

ue t Torq Inpu

Delivery Deliver

Overall Efficiency

Volum olumeetric tric Efficie Ef ncy

12,100 rpm

100

120

140

r powe Horse

wer rsepo ut Ho Outp

Input

e Torqu

Input

Overall Efficiency

Outlet Pressure

100

12,100 rpm

Horsepower Horsepower Loss Loss

100

120

140

100

wer Horsepo Output

sepower

Input Hor

orque put T

Efficiency Overall Efficiency

Outlet Pressure

Horsepower Horsepower

Efficiency - Percent

100

Input Torque - lb. ins. Input Torque - lb. ins.

3000

8100 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

100

120

140

100

120

140

Input Torque - lb. ins. Input Torque - lb. ins.

28 Efficiency - Percent

PV3-019

PV3-019 inches (mm)

2800

2900

2800

3000

2900

100

3100

4 Delivery - gpm

Delivery - gpm

Horsepower Loss

ut Ho Outp

ow rsep

er epow Hors Input

e rqu t To

Inpu

Overall Efficiency

Outlet Pressure

10,000 rpm

Horsepower Loss

rsepow Output Ho

30 er

rsepower Input Ho

20 0

5 0

15 10

100

120

140

160

180

200

100

120

140

160

180

200

ue t Torq Inpu

ncyy icieenc Effici Overall Eff

Outlet Pressure

Horsepower Horsepower

100

6600 rpm

Input Torque - lb. ins. Input Torque - lb. ins.

3000

( P) Outlet Pressure - psi

2800

400

800

1200

1600 2000 ( P) Outlet Pressure - psi

2400

8 Delivery - gpm

5 Horsepower Loss

er pow orse ut H Outp

er epow Hors Input

ue t Torq Inpu

35 60

0 3200

Overall Efficiency Efficiency

Outlet Pressure

12,500 rpm

2800

Horsepower Loss

Delivery Deliver

wer Horsepo Output

2900

100

25 20 wer orsepo Input H

e Torqu

Input

ienccyy Efficcien Overall Effi

Volumetric Efficiency

3000

Efficiency - Percent

3100

45 40

100

10,000 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

100

120

140

160

180

200

100

120

140

160

180

200

Input Torque - lb. ins. Input Torque - lb. ins.

30 Efficiency - Percent

PV3-022

PV3-022 inches (mm)

4 Delivery - gpm

3000

Delivery - gpm

10 Horsepower Loss

rse t Ho utpu

pow

r owe rsep t Ho Inpu

ue orq ut T Inp

Overall Efficiency

Outlet Pressure

100

3100

9000 rpm

Horsepower Loss

14 12

wer

rse

er pow

po orse

t Ho

ut H

Outp

Inpu

ue Torq

t Inpu

ienccyy ficien Effic Overall Ef

Outlet Pressure

Horsepower Horsepower

100

120

140

160

180

100

120

140

160

Input Torque - lb. ins. Input Torque - lb. ins.

3000

6000 rpm

400

800

1200

1600

2000

2400

8 Delivery - gpm

10 Horsepower Loss

er epow Hors Input w o er rsep u t Ho Outp

rque t To Inpu

Outlet Pressure Overall Efficiency

11,250 rpm

( P) Outlet Pressure - psi

2800

0 3200

100

3000

Horsepower Loss

Delivery Deliver

er w rsepo

ut Ho

Outp

r powe Horse Input

e rqu t To Inpu

Volumetric Efficiency

ienccyy Efficcien Overall Effi

3100

Efficiency - Percent

100

9000 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

100

120

140

160

180

100

120

140

160

180

Input Torque - lb. ins. Input Torque - lb. ins.

32 Efficiency - Percent

PV3-032

PV3-032 inches (mm)

2800

2900

t Ho utpu

3000

Delivery - gpm

10 Horsepower Loss

owe

p orse

tH utpu

t Inpu

wer epo Hors

ue orq ut T Inp

Overall Efficiency

Outlet Pressure

8000 rpm

8 Delivery - gpm

100

3100

Horsepower Loss

owe

r owe

rsep

t Ho

Inpu

28 ue Torq

ienccyy ficien Effic Overall Ef

Outlet Pressure

Horsepower Horsepower

100

120

140

160

180

120

160

200

240

280

320

360

400

Input Torque - lb. ins. Input Torque - lb. ins.

3000

800

1200

1600

2000

2400

8 Delivery - gpm

0 3200

20 Horsepower Loss

er epow Hors Input w o er rsep u t Ho Outp

rque t To Inpu

Overall Efficiency

Outlet Pressure

2800

10,000 rpm

( P) Outlet Pressure - psi

100

3000

Horsepower Loss

30 Delivery Deliver

e Torqu Input

er p ow

epow rs ut Ho Outp

400

ienccyy Efficcien Overall Effi

Volumetric Efficiency

rse t Ho Inpu

8000 rpm

3100

90 80

100

Efficiency - Percent

5300 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

100

120

140

160

180

120

160

200

240

280

320

360

400

Input Torque - lb. ins. Input Torque - lb. ins.

34 Efficiency - Percent

PV3-044

PV3-044 inches (mm)

3000

3100

8 Delivery - gpm

Delivery - gpm

epowe t Hors

Horsepower Loss

Outpu

10 0

120

160

200

240

280

120

160

200

240

280

40 wer

orsepo

Input H

que t Tor Inpu

Overall Efficiency

Outlet Pressure

8800 rpm

100

10 Horsepower Horsepower Loss Loss

16 12

wer epo Hors

ut Outp

24 20

rsep

60 t Ho

r owe

que t Tor Inpu

Inpu

Overall Efficiency

Outlet Pressure

Horsepower Horsepower

500

1000

1500

2000

3000

100

16 Delivery - gpm

2500

Horsepower Loss

er epow t Hors Inpu e w r rsepo ut Ho Outp

ue orq ut T Inp

Overall Efficiency

Outlet Pressure

11,000 rpm

( P) Outlet Pressure - psi

orsepo

wer

3000

Horsepower Loss

H Output

3500

orsepow

Input H

Overall Efficiency Delivery rque t To u p In

Volumetric Efficiency

8800 rpm

100

3100

Efficiency - Percent

100

Input Torque - lb. ins. Input Torque - lb. ins.

3000

5900 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

120

160

200

240

280

120

160

200

240

280

Input Torque - lb. ins. Input Torque - lb. ins.

36 Efficiency - Percent

PV3-049

PV3-049 inches (mm)

8 Delivery - gpm

3000

24 28

Delivery - gpm

Horsepower Loss

160

200

240

280

120

320

Overall Efficiency ue orq ut T er Inp ow ep ors tH u Inp er pow rse Ho t tpu Ou

Outlet Pressure

120

160

200

240

280

320

360

400

100

3100

8200 rpm

Horsepower Loss

pow

orse

ut H

Outp

Inpu

rque t To Inpu r owe sep Hor

ienccyy ficien Effic Overall Ef

Outlet Pressure

Horsepower Horsepower

100

Input Torque - lb. ins. Input Torque - lb. ins.

3000

5500 rpm

400

800

1200

1600

2000

2400

16 Delivery - gpm

10 Horsepower Loss

r owe rsep t Ho u p In er pow orse ut H Outp

ue orq ut T Inp

2800

Outlet Pressure

Overall Efficiency

10,250 rpm

( P) Outlet Pressure - psi

100

3000

0 3200

Horsepower Loss

Delivery Deliver

ue t Torq Inpu r e w o rsep t Ho Inpu er w o p rse ut Ho Outp

Volumetric olumetric Efficiency Ef

ienccyy Efficcien Overall Effi

3100

Efficiency - Percent

100

8200 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

120

160

200

240

280

320

120

160

200

240

280

320

Input Torque - lb. ins. Input Torque - lb. ins.

38 Efficiency - Percent

PV3-056

PV3-056 inches (mm)

2800

10 Delivery - gpm

powe

r ue

t Torq

Inpu

Delivery - gpm

Horsepower Loss 24 28

30 20

ower rsep ut Ho Outp

Input

100

Horse

Overall Ef Efficiency ficiency

Outlet Pressure

7000 rpm

3000

2900

100

3100

10 Horsepower Loss

rque t To

100

200

300

400

500

600

700

800

900

1000

100

150

200

250

300

350

400

450

500

400

800

1200

1600

Delivery Deliver

2000

2400

16 Delivery - gpm

50 0

100

150

200

250

300

350

400

450

500

100

0 3200

10 Horsepower Loss

r owe rsep t Ho er w o p orse ut H Outp Inpu

ue orq ut T Inp

cy Ef Overall Efficien

Outlet Pressure

2800

8750 rpm

( P) Outlet Pressure - psi

100

200

300

400

500

600

700

800

900

1000

100

3000

30 20

Horsepower Loss

power

e t Hors Outpu

rque Input To

50 we orsepo Input H

100

ienccyy Efficcien Overall Effi

Volumetric Efficiency

3100

7000 rpm

45 40

100

Efficiency - Percent

Inpu

r owe rsep t Ho Inpu er pow orse ut H tp u O

ienccyy ficien Effic Overall Ef

Outlet Pressure

2900

100

3000

4700 rpm

Input Torque - lb. ins. Input Torque - lb. ins.

3100

Efficiency - Percent

Horsepower Horsepower

Delivery - gpm ( P) Outlet Pressure - psi

Horsepower Horsepower

( P) Outlet Pressure - psi

Input Torque - lb. ins. Input Torque - lb. ins.

40 Efficiency - Percent

PV3-075

PV3-075 inches (mm)

2800

100

Delivery - gpm

24 28

10 Horsepower Loss

100

200

300

500

600

400

r powe Horse Input wer rsepo o H t u Outp

700

800

900

1000

100

200

300

400

500

600

700

800

900

1000

70 ue t Torq Inpu

Overall Ef Efficiency ficiency

Outlet Pressure

6000 rpm

16 Delivery - gpm

2800

Horsepower Loss

100

3000

er epow Hors Input wer rsepo ut Ho Outp

3100

2900

60 Inpu

70 ue Torq

100

cy cienncy Effificie Overall Ef

Outlet Pressu

2800

2900

100

3000

0 0

400

800

1200

1600

2000

2400

20 Delivery - gpm

7500 rpm

( P) Outlet Pressure - psi

Horsepower Loss

r owe rsep t Ho Inpu e Torqu Input er w o p rse t Ho utpu

Overall Efficiency

Outlet Pressure

2800

100

0 3200

10 Horsepower Loss

Delivery Deliver

e Torqu Input er epow Hors Input wer o p e rs ut Ho Outp

100

3100

ienccyy Efficcien Overall Effi

Volumetric olumetric Efficiency Ef

6000 rpm

100

Efficiency - Percent

4000 rpm

2900

100

3000

( P) Outlet Pressure - psi

Input Torque - lb. ins. Input Torque - lb. ins.

3100

Efficiency - Percent

Horsepower Horsepower

Delivery - gpm ( P) Outlet Pressure - psi

100

200

300

400

500

600

700

800

900

1000

100

200

300

400

500

600

700

800

900

1000

Input Torque - lb. ins. Input Torque - lb. ins.

42 Efficiency - Percent

PV3-115

PV3-115 inches (mm)

16 Delivery - gpm

3000

Delivery - gpm

100

Horsepower Loss

200

300

90 80

100

3000

3100

500

600

700

800

0 0

400

800

1200

1600

2000

32 Delivery - gpm

Input

Horsepower Loss

er epow

wer rsepo

ue orq ut T Inp

cy Ef Overall Efficien

Outlet Pressure

rs ut Ho Outp

7500 rpm

( P) Outlet Pressure - psi

2400

2800

100

3200

10 Horsepower Loss

Delivery Deliver

ienccyy Efficcien Overall Effi e orqu T t u Inp r owe rsep t Ho Inpu r e pow orse ut H Outp

Volumetric Efficiency

400

ue orq ut T Inp er ow ep ors tH er u Inp pow rse Ho t u tp Ou

Overall Efficiency

Outlet Pressure

100

200

300

400

500

600

700

800

100

3100

6000 rpm

Horsepower Loss

er pow orse ut H Outp

t Inpu

wer epo Hors

rque t To Inpu

ncy Overall Efficie

Outlet Pressure

Horsepower Horsepower

100

Input Torque - lb. ins. Input Torque - lb. ins.

3000

6000 rpm

Horsepower Horsepower

3100

( P) Outlet Pressure - psi

Delivery - gpm ( P) Outlet Pressure - psi

Efficiency - Percent

Efficiency - Percent Efficiency - Percent

4000 rpm

100

200

300

400

500

600

700

800

100

200

300

400

500

600

700

800

Input Torque - lb. ins.

44 Input Torque - lb. ins.

PV3-150 & PV3-160

PV3-150 & PV3-160 inches (mm)

2800

3000

2800

20 Delivery - gpm

100

Delivery - gpm

200

300

Horsepower Loss

400

500

600

700

800

900

100

Overall Efficiency er ow ue ep orq ors H tu T r ut we Inp Inp po rse Ho t tpu Ou

Outlet Pressure

5900 rpm

100

200

300

400

500

600

700

800

900

1000

100

3100

2900

Horsepower Loss

r owe rsep t Ho Inpu er pow orse ut H Outp

ue orq ut T Inp

100

ncy Overall Efficie

Outlet Pressure

2900

100

Horsepower Horsepower

4000 rpm

Input Torque - lb. ins. Input Torque - lb. ins.

3000

( P) Outlet Pressure - psi

2800

100

2900

400

800

1200

1600

2000

owe rsep

40 Delivery - gpm

Horsepower Loss

er pow orse ut H Outp

t Ho Inpu

e qu Tor ut Inp

ncyy cieenc Effici Overall Effi

Outlet Pressure

7400 rpm

( P) Outlet Pressure - psi

2400

2800

100

120

140

160

180

200

3200

10 0

Horsepower Loss

100

Delivery Deliver

cy ficienncy Efficie Overall Ef e er rqu o T pow t rse Inpu t Ho Inpu r owe sep Hor put Out

Volumetric Efficiency

3000

Efficiency - Percent

3100

90 80

100

5900 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

100

200

300

400

500

600

700

800

900

1000

100

200

300

400

500

600

700

800

900

1000

Input Torque - lb. ins. Input Torque - lb. ins.

46 Efficiency - Percent

PV3-205

PV3-205 inches (mm)

3000

Outlet Pressure

Delivery - gpm

200

Horsepower Loss

400

30 40

800

1000

1200

1400

100

120

90 80

100

3000

3100

600

Outp

er epow t Hors

ue t Torq Inpu er epow t Hors Inpu

Overall Efficiency

200

400

600

800

1000

1200

100

3100

5300 rpm

32 Delivery - gpm

Horsepower Loss

r we po rse Ho ut p In er pow rse Ho t tpu Ou

ficiency Overall Ef ue orq ut T Inp

3000

Horsepower Horsepower

Outlet Pressure

Input Torque - lb. ins. Input Torque - lb. ins.

100

Efficiency - Percent

3550 rpm

400

800

1200

32 Delivery - gpm

6600 rpm

( P) Outlet Pressure - psi

1600

5300 rpm

2000

2400

Horsepower Loss

r powe Horse Input wer rsepo ut Ho Outp

que t Tor Inpu

ficienccyy Efficien Overall Ef

100

120

140

100

120

3200

Outlet Pressure

2800

Horsepower Loss

Delivery Deliver

r powe Horse Input r e w o ep t Hors Outpu

ue t Torq Inpu

cy ficienncy Efficie Overall Ef

Volumetric Efficiency

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

200

400

600

800

1000

1200

1400

200

400

600

800

1000

1200

1400 Input Torque - lb. ins. Input Torque - lb. ins.

48 Efficiency - Percent

PV3-240

PV3-240 inches (mm)

2800

2900

3000

2800

50 60

0 40

Delivery - gpm

200

10 0

400

Horsepower Loss

600

1000 800

1200

1400

1600

1800

2000

160

180

200

ue 140 t Torq Inpu

Overall Efficiency

Outlet Pressure

er 120 epow t Hors Inpu wer 100 rsepo ut Ho Outp 80

5250 rpm

40 Delivery - gpm

Horsepower Loss

200

400

600

800

1000

1200

1400

1600

1800

2000

100

ut H Outp

3100

2900

pow orse

100

pow

140

160

Inpu

qu Tor

180

200

120

rse t Ho

Inp

ncyy ficienc Efficie Overall Ef

Outlet Pressure

Horsepower Horsepower

100

3000

2800

100

2900

1600

2000

2400

Horsepower Loss

80 Delivery - gpm

Horsepower Los

r we po rse er Ho t ow u ep Inp ors tH u tp Ou ue orq ut T Inp

ficienccyy Efficien Overall Ef

Outlet Pressure

6550 rpm

( P) Outlet Pressure - psi

100

120

140

2800

3200

160

100

120

140

160

180

200

1200

800

100

120

140

160

180

200

400

r owe rsep t Ho Inpu er w o rsep t Ho utpu

rque t To Inpu Delivery Deliver

cy ficienncy Efficie Overall Ef

Volumetric Efficiency

5250 rpm

3100

90 80

100

Efficiency - Percent

3500 rpm

Input Torque - lb. ins. Input Torque - lb. ins.

3000

( P) Outlet Pressure - psi

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

500

1000

1500

2000

2500

200

400

600

800

1000

1200

1400

1600

1800

2000

Input Torque - lb. ins. Input Torque - lb. ins.

50 Efficiency - Percent

PV3-300

PV3-300 inches (mm)

2800

2900

2800

3000

2900

100

3100

Delivery - gpm

Horsepower Loss

r we epo ors tH u tp Ou

Overall Efficiency ue orq r ut T we Inp po e s or H ut Inp

Outlet Pressure

100

Horsepower Loss

5550 rpm

40 Delivery - gpm

Inp

u orq ut T

r owe rsep t Ho Inpu wer rsepo ut Ho Outp

ncyy ficienc Efficie Overall Ef

Outlet Pressure

120

140

160

100

150

200

250

100

150

200

250

Horsepower Horsepower

100

500

1000

1500

2000

2500

500

1000

1500

2000

2500

Input Torque - lb. ins. Input Torque - lb. ins.

3000

( P) Outlet Pressure - psi

2800

2900

100

3000

3100

90 80

100

Efficiency - Percent

3700 rpm

400

800

1200

2000

80 Delivery - gpm

100

Horsepower Los

ue er ow orq ep ut T ors Inp tH u r Inp we epo ors tH u tp Ou

ficienccyy Efficien Overall Ef

Outlet Pressure

6900 rpm

( P) Outlet Pressure - psi

1600

5550 rpm

120

2400

140

2800

Horsepower Loss

er p ow orse ut H Outp

rque t To Inpu wer o rsep t Ho Inpu

Delivery Deliver

cy ficienncy Efficie Overall Ef

Volumetric Efficiency

0 160

100

150

200

250

0 3200

100

150

200

250

Horsepower Horsepower

3100

Efficiency - Percent

Delivery - gpm ( P) Outlet Pressure - psi

500

1000

1500

2000

2500

500

1000

1500

2000

2500

Input Torque - lb. ins. Input Torque - lb. ins.

52 Efficiency - Percent

PV3-375

PV3-375 inches (mm)

2800

500

1000

1500

3500

Discharge Pressure - psig

0 3000

0 4000

2500

2000

Horsepower Loss

100

120

e Torqu Input

140

160

r we epo ors ut H p t u

ut Inp

er pow rse Ho

ficiency Overall Ef

180

200

Volumetric olumetric Ef Efficiency

Outlet Flow

0 60

100

4400 rpm

30 Delivery - gpm

er pow rse Ho

Horsepower Loss

t tpu Ou

ut Inp

epo

s Hor

ncy Overall Efficie e rqu o T ut Inp

100

400

800

1200

1600

2000

2400

2800

3200

3600

4000

200

400

600

800

1000

1200

1400

1600

1800

2000

2800

400

800

1200

1600

2000

2400

50 Delivery - gpm

100

400 0

800

1200

1600

2000

2400

2800

3200

3600

4000

400

800

1200

1600

2000

2400

2800

3200

3600

4000

60 Horsepower Loss

30 20

120

140

160

180

200

0 3200

ue t Torq Inpu

Outlet Pressure wer epo ors ut H icieennccyy Efffici Inp Overall Ef r owe sep r o H put Out

2800

100

5500 rpm

( P) Outlet Pressure - psi

100

Horsepower Loss

100

er epow t Hors Outpu

r powe Horse Input

3000 2900

Outlet Flow

120

140

180

200

160

e Torqu Input

Ef iency Overall Effic

Volumetric olumetric Ef Efficiency

3100

4400 rpm

90 80

100

Efficiency - Percent

Outlet Pressure

2900

100

Horsepower Horsepower

3000

Input Torque - lb. ins. Input Torque - lb. ins.

3000 rpm

Horsepower Horsepower

3100

( P) Outlet Pressure - psi

Outlet Flow

Efficiency - Percent

Outlet Flow ( P) Outlet Pressure - psi

Input Torque - lb. ins. Input Torque - lb. ins.

54 Efficiency - Percent

PV3-400

PV3-400 inches (mm)

2800

2900

2800

30 40 Delivery - gpm

Delivery - gpm

0 80

0 100

Horsepower Loss

120

que t Tor Inpu

140

160

180

200

100

owe

sep

or ut H

t Ho

Out

Inpu

ow rsep

Overall Efficiency

Outlet Pressure

4100 rpm

3000

2900

100

3100

10 Horsepower Loss

100

er pow orse ut H Outp

120

que t Tor Inpu r w po e orse put H

140

160

Overall Efficiency

180

200

400

800

1200

1600

2000

2400

2800

3200

3600

4000

400

800

1200

1600

2000

2400

2800

3200

3600

4000

2000

2400

60 Delivery - gpm

100

Horsepower Loss

120

160

200

400 0

800

1200

1600

2000

2400

2800

3200

3600

4000

400

800

1200

1600

2000

2400

2800

3200

3600

4000

po w e

120

Horse

epow

ut Outp

Hors

240

280

320

360

400

Input

e orqu put T

icieennccyy Effici Overall Eff

Outlet Pressure

5125 rpm

2800

0 3200

100

2800

1600 ( P) Outlet Pressure - psi

3000 2900

1200

40 Horsepower Loss

20 10

120

140

160

800

r owe

180

200

100

400

rsep t Ho

r owe sep Hor put t u e u O Torq Input

Inpu

Outlet Flow

Volumetric olumetric Ef Efficiency cy ficienncy Efficie Overall Ef

4100 rpm

3100

90 80

100

Efficiency - Percent

Outlet Pressure

Horsepower Horsepower

100

Input Torque - lb. ins. Input Torque - lb. ins.

3000

2750 rpm

Horsepower Horsepower

3100

Efficiency - Percent

Outlet Flow ( P) Outlet Pressure - psi

( P) Outlet Pressure - psi

Input Torque - lb. ins. Input Torque - lb. ins.

56 Efficiency - Percent

PV3-488

PV3-488 inches (mm)

pressure - kPa

2000

4000

6000

8000

10,000

12,000

14,000

16,000

18,000

20,000

pressure - bar

flow - L/min

120

160

200

240

100

120

140

160

180

200

220

pressure - psi

15 flow - gpm

no. of L/min = 3.785 x no. of gpm

1000

no. of bar = .06895 x no. of psi no. of kPa = 6.895 x no. of psi

no. of gpm = 0.2642 x no. of L/min

2000

no. of psi = 14.50 x no. of bar no. of psi = .145 x no. of kPa

3000

torque = N•m volume - mL (cc)

22,000

120

160

200

240

volume - in 3

140

no. of in3 = 0.06102 x no. of mL

120

no. of lb-in = 8.851 x no. of N•m

80 100 torque = lb - in

no. of mL = 16.39 x no. of in3

no. of N•m = 0.1130 x no. of lb-in

160

Metric Conversion of Hydraulic Units

recommended inlet pressure - psia 50

speed - rpm x 10

160 PV3-11 5

& PV3-

PV3 -011 &

PV3-15 0

PV3 -022

PV3-03 2

044

PV3-

60 PV3-05 6

80 PV3-07 5

-00

70 PV3

& PV3-4

90 PV3-30 0 & PV 3-375 PV3-20 5 & PV 3-240

PV3-400

Inlet Pressures

100

-3

Eaton Aerospace Worldwide Eaton Aerospace is a worldwide supplier of advanced technology hydraulic, electrohydraulic and electronic power and motion control components and systems for aerospace, marine and defense applications. Eaton Aerospace has major manufacturing and service centers located in the United States, United Kingdom, and Asia, which are supported by a worldwide network of sales and service offices. The strategic location of Eaton Aerospace design engineering, product support and production facilities throughout the world ensures that it will remain responsive to its customers needs. Reliable products and comprehensive product support have made Eaton Aerospace the world leader in aerospace, marine and defense fluid power, motion and control applications.

Vickers Fluid Systems of Eaton Aerospace is a worldwide leader in advanced technology fluid power and fuel pump products serving the aerospace, marine and defense markets. / Vickers Fluid Systems designs and manufactures power and motion control components and systems for customers worldwide. Eaton Aerospace is a business group of Eaton Corporation, the pioneer and world leader in power and motion control. / In addition to Vickers Fluid Systems, the Eaton Aerospace Operations includes the Actuation and Controls, Sterer Engineering, Power and Load Management Systems, Cockpit Controls and Displays and Engineered Sensors/Tedeco Business Units. Combining the core technologies of these business units Eaton Aerospace provides virtually every power, motion control and monitoring product and service needed by aerospace, marine and defense customers the world over. 60

Global Locations United States (headquarters) Eaton Aerospace Worldwide Operations 3 Park Plaza, Suite 1200 Irvine, CA 92614 USA Phone: (949) 253-2100 Fax: (949) 253-2111 Eaton Aerospace Vickers Fluid Systems 5353 Highland Drive Jackson, MS 39206-3449 USA Phone: (601) 981-2811 Fax: (601) 987-5255 SITA: JANVKXD Eaton Aerospace Sterer Engineering 4690 Colorado Boulevard Los Angeles, CA 90039 USA Phone: (818) 409-0200 Fax: (818) 241-3772 Eaton Aerospace Vickers Actuation and Controls 3675 Patterson Avenue P.O. Box 872 Grand Rapids, MI 49588-0872 USA Phone: (616) 949-1090 Fax: (616) 949-2744 Eaton Aerospace Engineered Sensors/Tedeco 24 East Glenolden Avenue Glenolden, PA 19036 USA Phone: (610) 583-9400 Fax: (610) 583-3985

Eaton Aerospace Power and Load Management Systems 2250 Whitfield Avenue Sarasota, FL 34243 USA Phone: (941) 751-7138 Fax: (941) 751-7173 Eaton Aerospace Cockpit Controls and Displays 1640 Monrovia Avenue Costa Mesa, CA 92627 USA Phone: (949) 642-2427 Fax: (949) 722-4487 Eaton Aerospace Engineered Sensors/Tedeco 15 Durant Avenue Bethel, CT 06801 USA Phone: (800) 736-1557 Fax: (203) 796-6313 France Eaton Aerospace Aeroquip-Vickers S.A. Le Parc Club des Septs Deniers Bat 2 78, Chemin des Septs-Deniers 31200 Toulouse France Phone: (33) 5 61573-333 Fax: (33) 5 61578-777 Germany Eaton Aerospace Aeroquip-Vickers International GmbH Am Joseph 16 61273 Wehrheim Germany Phone: (49) 6081-103220 or 230 Fax: (49) 6081-103229 or 239

Italy Eaton Aerospace Aeroquip-Vickers S.p.A. Via Monzese 34 Vignate, Milan 20060 Italy Phone: (39) 02 95058222 Fax: (39) 02 9566730 Philippines Eaton Aerospace 9A LPL Plaza, 124 Alfaro Street Salcedo Village, Makati City Philippines Phone: (63-2) 816 0148 Fax: (63-2) 815 3348 United Kingdom Eaton Aerospace Vickers Systems Limited Larchwood Avenue Bedhampton Hampshire PO9 3QN England Phone: (44) 1705-487260 Fax: (44) 1705-492400

Visit the Eaton Aerospace web site at http://www.aerospace.eaton.com

Eaton Aerospace Vickers Fluid Systems 5353 Highland Drive Jackson, MS 39206-3449