Danfoss RE User guide

Technical Information

Orbital Motors

Type RE

powersolutions.danfoss.com

2 | © Danfoss | May 2018

BC267979667405en-000101

TABLE OF CONTENTS
TECHNICAL INFORMATION
Operating Recommendations.......................................................................................................................................		4-5
Motor Connections...........................................................................................................................................................		5
Product Testing (Understanding the Performance Charts)..............................................................................................		6
Allowable Bearing & Shaft Loads.....................................................................................................................................		7
Vehicle Drive Calculations.............................................................................................................................................		8-9
Induced Side Loading....................................................................................................................................................		10
Hydraulic Equations.......................................................................................................................................................		10
Shaft Nut Dimensions & Torque Specifications...............................................................................................................		11
OPTIONAL MOTOR FEATURES
Speed Sensor Options..............................................................................................................................................		12-13
Freeturning Rotor Option...............................................................................................................................................		13
Internal Drain..................................................................................................................................................................		14
Hydraulic Declutch.........................................................................................................................................................		14
Valve Cavity Option........................................................................................................................................................		15
Slinger Seal Option........................................................................................................................................................		15
MEDIUM DUTY HYDRAULIC MOTORS
RE Product Line Introduction.........................................................................................................................................		16
RE Displacement Performance Charts.....................................................................................................................		17-22
505	& 506 Series Housings.......................................................................................................................................	23-24
505	& 506 Series Technical Information.........................................................................................................................	25
505	& 506 Series Shafts................................................................................................................................................	26
505	& 506 Series Ordering Information..........................................................................................................................	27
520	& 521 Series Housings............................................................................................................................................	28
520	& 521 Series Technical Information.........................................................................................................................	29
520	& 521 Series Shafts................................................................................................................................................	30
520	& 521 Series Ordering Information..........................................................................................................................	31
530	& 531 Series Housings............................................................................................................................................	32
530	& 531 Series Technical Information.........................................................................................................................	33
530	& 531 Series Shafts................................................................................................................................................	34
530	& 531 Series Ordering Information..........................................................................................................................	35
535	& 536 Series Housings............................................................................................................................................	36
535	& 536 Series Technical Information.........................................................................................................................	36
535	& 536 Series Shafts................................................................................................................................................	37
535	& 536 Series Ordering Information..........................................................................................................................	37
540	& 541 Series Housings............................................................................................................................................	38
540	& 541 Series Technical Information.........................................................................................................................	39
540	& 541 Series Ordering Information..........................................................................................................................	39

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OPERATING RECOMMENDATIONS

OIL TYPE

Hydraulic oils with anti-wear, anti-foam and demulsifiers are recommended for systems incorporating Danfoss motors. Straight oils can be used but may require VI (viscosity index) improvers depending on the operating temperature range of the system. Other water based and environmentally friendly oils may be used, but service life of the motor and other components in the system may be significantly shortened. Before using any type of fluid, consult the fluid requirements for all components in the system for compatibility. Testing under actual operating conditions is the only way to determine if acceptable service life will be achieved.

FLUID VISCOSITY & FILTRATION

Fluids with a viscosity between 20 - 43 cSt [100 - 200 S.U.S.] at operating temperature is recommended. Fluid temperature should also be maintained below 85°C [180° F]. It is also suggested that the type of pump and its operating specifications be taken into account when choosing a fluid for the system. Fluids with high viscosity can cause cavitation at the inlet side of the pump. Systems that operate over a wide range of temperatures may require viscosity improvers to provide acceptable fluid performance.

Danfoss recommends maintaining an oil cleanliness level of ISO 17-14 or better.

INSTALLATION & START-UP

When installing a Danfoss motor it is important that the mounting flange of the motor makes full contact with the mounting surface of the application. Mounting hardware of the appropriate grade and size must be used. Hubs, pulleys, sprockets and couplings must be properly aligned to avoid inducing excessive thrust or radial loads. Although the output device must fit the shaft snug, a hammer should never be used to install any type of output device onto the shaft. The port plugs should only be removed from the motor when the system connections are ready to be made. To avoid contamination, remove all matter from around the ports of the motor and the threads of the fittings. Once all system connections are made, it is recommended that the motor be run-in for 15-30 minutes at no load and half speed to remove air from the hydraulic system.

MOTOR PROTECTION

Over-pressurization of a motor is one of the primary causes of motor failure. To prevent these situations, it is necessary to provide adequate relief protection for a motor based on the pressure ratings for that particular model. For systems that may experience overrunning conditions, special precautions must be taken. In an overrunning condition, the motor functions as a pump and attempts to convert kinetic energy into hydraulic energy. Unless the system is properly

configured for this condition, damage to the motor or system can occur. To protect against this condition a counterbalance valve or relief cartridge must be incorporated into the circuit to reduce the risk of overpressurization. If a relief cartridge is used, it must be installed upline of the motor, if not in the motor, to relieve the pressure created by the over-running motor. To provide proper motor protection for an over-running load application, the pressure setting of the pressure relief valve must not exceed the intermittent rating of the motor.

HYDRAULIC MOTOR SAFETY PRECAUTION

A hydraulic motor must not be used to hold a suspended load. Due to the necessary internal tolerances, all hydraulic motors will experience some degree of creep when a load induced torque is applied to a motor at rest. All applications that require a load to be held must use some form of mechanical brake designed for that purpose.

MOTOR/BRAKE PRECAUTION

Caution! - Danfoss motor/brakes are intended to operate as static or parking brakes. System circuitry must be designed to bring the load to a stop before applying the brake.

Caution! - Because it is possible for some large displacement motors to overpower the brake, it is critical that the maximum system pressure be limited for these applications. Failure to do so could cause serious injury or death. When choosing a motor/brake for an application, consult the performance chart for the series and displacement chosen for the application to verify that the maximum operating pressure of the system will not allow the motor to produce more torque than the maximum rating of the brake. Also, it is vital that the system relief be set low enough to insure that the motor is not able to overpower the brake.

To ensure proper operation of the brake, a separate case drain back to tank must be used. Use of the internal drain option is not recommended due to the possibility of return line pressure spikes.Asimple schematic of a system utilizing a motor/brake is shown on page 4. Although maximum brake release pressure may be used for an application, a

34 bar [500 psi] pressure reducing valve is recommended to promote maximum life for the brake release piston seals.

However, if a pressure reducing valve is used in a system which has case drain back pressure, the pressure reducing valve should be set to 34 bar [500 psi] over the expected case pressure to ensure full brake release. To achieve proper brake release operation, it is necessary to bleed out any trapped air and fill brake release cavity and hoses before all connections are tightened. To facilitate this operation, all motor/brakes feature two release ports. One or both of these ports may be used to release the brake in the

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OPERATING RECOMMENDATIONS & MOTOR CONNECTIONS

MOTOR/BRAKE PRECAUTION (continued)

unit. Motor/brakes should be configured so that the release ports are near the top of the unit in the installed position.

TYPICAL MOTOR/BRAKE SCHEMATIC

Once all system connections are made, one release port must be opened to atmosphere and the brake release line carefully charged with fluid until all air is removed from the line and motor/brake release cavity. When this has been accomplished the port plug or secondary release line must be reinstalled. In the event of a pump or battery failure, an external pressure source may be connected to the brake release port to release the brake, allowing the machine to be moved.

MOTOR CIRCUITS

There are two common types of circuits used for connecting multiple numbers of motors – series connection and parallel connection.

SERIES CONNECTION

When motors are connected in series, the outlet of one motor is connected to the inlet of the next motor. This allows the full pump flow to go through each motor and provide maximum speed. Pressure and torque are distributed between the motors based on the load each motor is subjected to. The maximum system pressure must be no greater than the maximum inlet pressure of the first motor.The allowable back pressure rating for a motor must also be considered. In some series circuits the motors must have an external case drain connected. A series connection is desirable when it is important for all the motors to run the same speed such as on a long line conveyor.

SERIES CIRCUIT

PARALLEL CONNECTION

In a parallel connection all of the motor inlets are connected.

This makes the maximum system pressure available to each motor allowing each motor to produce full torque at that pressure. The pump flow is split between the individual motors according to their loads and displacements. If one motor has no load, the oil will take the path of least resistance and all the flow will go to that one motor. The others will not turn. If this condition can occur, a flow divider is recommended to distribute the oil and act as a differential.

NOTE: It is vital that all operating recommendations be followed. Failure to do so could result in injury or death.

SERIES CIRCUIT

NOTE: The motor circuits shown above are for illustration purposes only. Components and circuitry for actual applications may vary greatly and should be chosen based on the application.

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PRODUCT TESTING

Performance testing is the critical measure of a motor’s ability to convert flow and pressure into speed and torque. All product testing is conducted using Danfoss state of the art test facility. This facility utilizes fully automated test equipment and custom designed software to provide accurate, reliable test data. Test routines are standardized, including test stand calibration and stabilization of fluid temperature and viscosity, to provide consistent data. The example below provides an explanation of the values pertaining to each heading on the performance chart.

080

76 cc [4.6 in3/rev.]

	<![if ! IE]> <![endif]>[gpm]lpm	4	[1]
		2 [0.5]
	<![if ! IE]> <![endif]>-
	<![if ! IE]> <![endif]>Flow	8	[2]
		15 [4]
		23 [6]
		1
		38	[10]
		45	[12]
	<![if ! IE]> <![endif]>Max. Cont.
		53	[14]
		61	[16]
	<![if ! IE]> <![endif]>Max. Inter.
		64	[17]

	Pressure - bars [psi]																Max. Cont.			Max. Inter.
	17 [250]		35 [500]		69 [1000]				104 [1500] 2138 [2000]						173 [2500]		207 [3000]			242 [3500]
	rque - Nm [lb-in], Speed rpm																Intermittent Ratings - 10% of Operation
6 14																								<![if ! IE]> <![endif]>Theoretical
		50		50		43				43				34		32		32			31		51
		[127]	30	[262]	61	[543]			91	[806]		120		[1062]	145	[1285]	169	[1496]		191	[1693]		26
		25		24		21				18				17		11		11			9
	16	[140]	32	[286]	63	[559]			95	[839]		124		[1099]	151	[1340]	178	[1579]		203	[1796]
	16	[139]	32	[280]	64	[563]			97	[857]		129		[1139]	157	[1390]	187	[1652]		211	[1865]		101	<![if ! IE]> <![endif]>rpm
100			100			99				92				87		79		78			77
	14	[127]	31	[275]	65	[572]			99	[872]		131		[1155]	160	[1420]	186	[1643]		216	[1911]		201
	200		200			199		7 96		191				181		174		160			154
	13	[113]	30	[262]	63	[557]				[853]		130		[1149]	160	[1420]	186	[1646]	3		[1930]		302
	301		300			297				295				284		271		253			245
	10	[91]	27	[243]	61	[536]		93		[826]		127		[1125]	159	[1409]	187	[1654]	220		[1945]		4
	401		400			398				390				384		372		346			339
			24	[212]	58	[511]			89	[790]		123		[1087]	156	[1379]	185	[1638]	213		[1883]		503
			502			500				499				498		485		443			433
			20	[177]	54	[482]			87	[767]		120		[1060]	164	[1451]	193	[1711]	228		[2021]		603
			602			601				600				597		540		526			510
			14	[127]	50	[445]			84	[741]		124		[1098]	155	[1369]	185	[1640]	217		[1918]		704
			690			689				5				658		644		631			613
																							804
																							904
	Overall Efficiency - 70 - 100%							40 - 69%						0 - 39%
	Theoretical Torque - Nm [lb-in]
	21 [183]		41 [366]		83 [732]				124 [1099] 8166 [1465]						207 [1831]		248 [2197]			290 [2564]

Displacement tested at 54°C [129°F] with an oil viscosity of 46cSt [213 SUS]

1.Flow represents the amount of fluid passing through the motor during each minute of the test.

2.Pressure refers to the measured pressure differential between the inlet and return ports of the motor during the test.

3.The maximum continuous pressure rating and maximum intermittent pressure rating of the motor are separated by the dark lines on the chart.

4.Theoretical RPM represents the RPM that the motor would produce if it were 100% volumetrically efficient.

Measured RPM divided by the theoretical RPM give the actual volumetric efficiency of the motor.

5.The maximum continuous flow rating and maximum intermittent flow rating of the motor are separated by the dark line on the chart.

6.Performance numbers represent the actual torque and speed generated by the motor based on the corresponding input pressure and flow. The numbers on the top row indicate torque as measured in Nm [lb-in], while the bottom number represents the speed of the output shaft.

7.Areas within the white shading represent maximum motor efficiencies.

8.Theoretical Torque represents the torque that the motor would produce if it were 100% mechanically efficient.

Actual torque divided by the theoretical torque gives the actual mechanical efficiency of the motor.

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ALLOWABLE BEARING & SHAFT LOADING

This catalog provides curves showing allowable radial loads at points along the longitudinal axis of the motor. They are dimensioned from the mounting flange. Two capacity curves for the shaft and bearings are shown.Avertical line through the centerline of the load drawn to intersect the x-axis intersects the curves at the load capacity of the shaft and of the bearing.

In the example below the maximum radial load bearing rating is between the internal roller bearings illustrated with a solid line. The allowable shaft rating is shown with a dotted line.

The bearing curves for each model are based on labratory analysis and testing results constructed at Danfoss. The shaft loading is based on a 3:1 safety factor and 330 Kpsi tensile strength. The allowable load is the lower of the curves at a given point. For instance, one inch in front of the mounting flange the bearing capacity is lower than the shaft capacity.

In this case, the bearing is the limiting load. The motor user needs to determine which series of motor to use based on their application knowledge.

ISO 281 RATINGS VS. MANUFACTURERS RATINGS

Published bearing curves can come from more than one type of analysis. The ISO 281 bearing rating is an international standard for the dynamic load rating of roller bearings. The rating is for a set load at a speed of 33 1/3 RPM for 500 hours (1 million revolutions). The standard was established to allow consistent comparisons of similar bearings between manufacturers. The ISO 281 bearing ratings are based solely on the physical characteristics of the bearings, removing any manufacturers specific safety factors or empirical data that influences the ratings.

Manufacturers’ ratings are adjusted by diverse and systematic laboratory investigations, checked constantly with feedback from practical experience. Factors taken into account that affect bearing life are material, lubrication, cleanliness of the lubrication, speed, temperature, magnitude of the load and the bearing type.

The operating life of a bearing is the actual life achieved by the bearing and can be significantly different from the calculated life. Comparison with similar applications is the most accurate method for bearing life estimations.

EXAMPLE LOAD RATING FOR MECHANICALLY RETAINED NEEDLE ROLLER BEARINGS

-100	-75	-50	-25	0	25	50	75	100	mm
9000									4000
8000									3500
						445 daN [1000 lb]
7000									3000
6000						445 daN [1000 lb]
									2500
5000
									2000
4000
									1500
3000
							SHAFT
2000									1000
1000					BEARING				500
lb									daN
-100	-75	-50	-25	0	25	50	75	100	mm

Bearing Life L	10	=	(C/P)p [106 revolutions]
L10		=	nominal rating life
C =			dynamic load rating
	P =		equivalent dynamic load
Life Exponent p =			10/3 for needle bearings

BEARING LOAD MULTIPLICATION FACTOR TABLE

RPM	FACTOR	RPM	FACTOR
50	1.23	500	0.62
100	1.00	600	0.58
200	0.81	700	0.56
300	0.72	800	0.50
400	0.66

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VEHICLE DRIVE CALCULATIONS

When selecting a wheel drive motor for a mobile vehicle, a number of factors concerning the vehicle must be taken into consideration to determine the required maximum motor RPM, the maximum torque required and the maximum load each motor must support. The following sections contain the necessary equations to determine this criteria. An example is provided to illustrate the process.

Sample application (vehicle design criteria)

vehicle description......................................				4 wheel vehicle
vehicle drive..................................................					2 wheel drive
GVW	..................................................................				1,500 lbs.
weight over each drive wheel			.................................		425 lbs.
rolling radius of tires...................................................					16 in.
desired acceleration..............................			0 -5 mph in 10 sec.
top speed.................................................................					5 mph
gradability....................................................................				20%
worst working surface.....................................					poor asphalt
To determine maximum motor speed				168 x MPH x G
RPM = 2.65 x KPH x G			RPM =
	rm				ri
Where:
MPH = max. vehicle speed (miles/hr)
KPH	= max. vehicle speed (kilometers/hr)
ri	= rolling radius of tire (inches)
G	= gear reduction ratio (if none, G = 1)
rm	= rolling radius of tire (meters)
	Example RPM =		168 x 5 x 1		= 52.5
			16

To determine maximum torque requirement of motor

To choose a motor(s) capable of producing enough torque to propel the vehicle, it is necessary to determine the Total Tractive Effort (TE) requirement for the vehicle. To determine the total tractive effort, the following equation must be used:

TE = RR + GR + FA + DP (lbs or N)

Where:

TE	= Total tractive effort
RR	= Force necessary to overcome rolling resistance
GR	= Force required to climb a grade
FA	= Force required to accelerate
DP	= Drawbar pull required

The components for this equation may be determined using the following steps:

Step One: Determine Rolling Resistance

Rolling Resistance (RR) is the force necessary to propel a vehicle over a particular surface. It is recommended that the worst possible surface type to be encountered by the vehicle be factored into the equation.

RR =	GVW x R (lb or N)
	1000

Where:

GVW= gross (loaded) vehicle weight (lb or kg)

R= surface friction (value from Table 1) Example RR = 15001000 x 22 lbs = 33 lbs

Table 1
Rolling Resistance
Concrete (excellent)	..............10
Concrete (good)....................	15
Concrete (poor).....................	20
Asphalt (good).......................	12
Asphalt (fair)..........................	17
Asphalt (poor)........................	22
Macadam (good)...................	15
Macadam (fair)......................	22
Macadam (poor)....................	37
Cobbles (ordinary).................	55
Cobbles (poor)......................	37
Snow (2 inch)........................	25
Snow (4 inch)........................	37
Dirt (smooth).........................	25
Dirt (sandy)............................	37
Mud............................	37 to 150
Sand (soft)..................	60 to 150
Sand (dune).............	160 to 300

Step Two: Determine Grade Resistance

Grade Resistance (GR) is the amount of force necessary to move a vehicle up a hill or “grade.” This calculation must be made using the maximum grade the vehicle will be expected to climb in normal operation.

To convert incline degrees to % Grade:

% Grade = [tan of angle (degrees)] x 100

GR =	% Grade	x GVW (lb or N)
	100
	Example	GR =	20		x 1500 lbs = 300 lbs
				100

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VEHICLE DRIVE CALCULATIONS

Step Three: Determine Acceleration Force

Acceleration Force (FA) is the force necessary to accelerate from a stop to maximum speed in a desired time.

FA =	MPH x GVW (lb)	FA =	KPH x GVW (N)
	22 x t		35.32 x t

Where:

t = time to maximum speed (seconds)

Example FA =	5 x 1500 lbs	= 34 lbs
	22 x 10

Step Four: Determine Drawbar Pull

Drawbar Pull (DP) is the additional force, if any, the vehicle will be required to generate if it is to be used to tow other equipment. If additional towing capacity is required for the equipment, repeat steps one through three for the towable equipment and sum the totals to determine DP.

Step Five: Determine Total Tractive Effort

The Tractive Effort (TE) is the sum of the forces calculated in steps one through three above. On low speed vehicles, wind resistance can typically be neglected.

However, friction in drive components may warrant the addition of 10% to the total tractive effort to insure acceptable vehicle performance.

Step Seven: Determine Wheel Slip

To verify that the vehicle will perform as designed in regards to tractive effort and acceleration, it is necessary to calculate wheel slip (TS) for the vehicle. In special cases, wheel slip may actually be desirable to prevent hydraulic system overheating and component breakage should the vehicle become stalled.

TS =	W x f x ri	TS =	W x f x rm
	G		G
(lb-in per motor)		(N-m per motor)

Where:

f= coefficient of friction (see table 2)

W = loaded vehicle weight over driven wheel (lb or N)

Example TS = 425 x .06 x 16 lb-in/motor = 4080 lbs 1

Table 2

Coefficient of friction (f)

Steel on steel........................................	0.3
Rubber tire on dirt.................................	0.5
Rubber tire on a hard surface.......	0.6 - 0.8
Rubber tire on cement...........................	0.7

TE = RR + GR + FA + DP (lb or N)

Example TE = 33 + 300 + 34 + 0 (lbs) = 367 lbs

Step Six: Determine Motor Torque

The Motor Torque (T) required per motor is the Total Tractive Effort divided by the number of motors used on the machine. Gear reduction is also factored into account in this equation.

T =	TE x ri	lb-in per motor	T =	TE x rm	Nm per motor
	M x G			M x G

Where:

M = number of driving motors

Example T = 367 x 16 lb-in/motor = 2936 lb-in 2 x 1

To determine radial load capacity requirement of motor

When a motor used to drive a vehicle has the wheel or hub attached directly to the motor shaft, it is critical that the radial load capabilities of the motor are sufficient to support the vehicle. After calculating the Total Radial Load (RL) acting on the motors, the result must be

compared to the bearing/shaft load charts for the chosen motor to determine if the motor will provide acceptable load capacity and life.

RL = W2 + ( riT )2	lb	RL = W2 + (	T	)2 kg
			rm
Example RL =		4252 + ( 293616 )2 = 463 lbs

Once the maximum motor RPM, maximum torque requirement, and the maximum load each motor must support have been determined, these figures may then be compared to the motor performance charts and to the bearing load curves to choose a series and displacement to fulfill the motor requirements for the application.

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INDUCED SIDE LOAD

In many cases, pulleys or sprockets may be used to transmit the torque produced by the motor. Use of these components will create a torque induced side load on the motor shaft and bearings. It is important that this load be taken into consideration when choosing a motor with sufficient bearing and shaft capacity for the application.

Radius 76 mm [3.00 in]

HYDRAULIC EQUATIONS

Multiplication Factor	Abbrev.	Prefix
1012	T	tera
109	G	giga
106	M	mega
103	K	kilo
102	h	hecto
101	da	deka
10-1	d	deci
10-2	c	centi
10-3	m	milli
10-6	u	micro
10-9	n	nano
10-12	p	pico
10-15	f	femto
10-18	a	atto

Torque

1129 Nm

[10000 lb-in]

To determine the side load, the motor torque and pulley or sprocket radius must be known. Side load may be calculated using the formula below. The distance from the pulley/sprocket centerline to the mounting flange of the motor must also be determined. These two figures may then be compared to the bearing and shaft load curve of the desired motor to determine if the side load falls within acceptable load ranges.

Theo. Speed (RPM) =
	1000 x LPM		or		231 x GPM
Displacement (cm3/rev)					Displacement (in3/rev)
Theo. Torque (lb-in) =
	Bar x Disp. (cm3/rev)		or	PSI x Displacement (in3/rev)
	20 pi			6.28

Distance

Torque

Side Load = Radius

Side Load = 14855 Nm [3333 lbs]

	Power In (HP) =
	Bar x LPM	or	PSI x GPM
	600		1714
	Power Out (HP) =
	Torque (Nm) x RPM	or	Torque (lb-in) x RPM
	9543		63024

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SHAFT NUT INFORMATION

35MM TAPERED SHAFTS

M24 x 1.5 Thread

A Slotted Nut

	6 [.24]
	6 [.22]
	42 [1.64]
36 [1.42]	15 [.59]
Torque Specifications:	32.5 daNm [240 ft.lb.]

PRECAUTION

The tightening torques listed with each nut should only be used as a guideline. Hubs may require higher or lower tightening torque depending on the material. Consult the hub manufacturer to obtain recommended tightening torque. To maximize torque transfer from the shaft to the hub, and to minimize the potential for shaft breakage, a hub with sufficient thickness must fully engage the taper length of the shaft.

incorrect

correct

1” TAPERED SHAFTS

3/4-28 Thread

A	Slotted Nut		B	Lock Nut				C	Solid Nut
		6 [.24]		23 [.92]			16 [.63]
		5 [.19]
		33 [1.29]		33 [1.29]		24 [.95]	28 [1.10]			33 [1.28]
	28 [1.12]	12 [.48]		29 [1.13]			3.5 [.14]		28 [1.11]	12 [.47]
Torque Specifications:		20 - 23 daNm [150 - 170 ft.lb.]	Torque Specifications:		24 - 27 daNm [180 - 200 ft.lb.]			Torque Specifications:		20 - 23 daNm [150 - 170 ft.lb.]
1-1/4” TAPERED SHAFTS
1-20 Thread
A	Slotted Nut		B	Lock Nut				C	Solid Nut
		6 [.25]		29 [1.14]			16 [.63]
		5 [.19]
		44 [1.73]		40 [1.57]		30 [1.18]	34 [1.34]			44 [1.73]
	38 [1.48]	14 [.55]		35 [1.38]			4 [.16]		38 [1.48]	14 [.55]
Torque Specifications:		38 daNm [280 ft.lb.] Max.	Torque Specifications:		33 - 42 daNm [240 - 310 ft.lb.]			Torque Specifications:		38 daNm [280 ft.lb.] Max.
1-3/8” & 1-1/2” TAPERED SHAFTS
1 1/8-18 Thread
A	Slotted Nut		B	Lock Nut				C	Solid Nut
		6 [.22]		35 [1.38]			16 [.63]
		5 [.19]
		48 [1.90]		51 [2.00]		36 [1.42]	44 [1.73]			48 [1.90]
	42 [1.66]	15 [.61]		44 [1.73]			4 [.16]		42 [1.66]	15 [.61]
Torque Specifications:		41 - 54 daNm [300 - 400 ft.lb.]	Torque Specifications:		34 - 48 daNm [250 - 350 ft.lb.]			Torque Specifications:		41 - 54 daNm [300 - 400 ft.lb.]

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SPEED SENSORS

Danfoss offers both single and dual element speed sensor options providing a number of benefits to users by incorporating the latest advancements in sensing technology and materials. The 700 & 800 series motors single element sensors provide 60 pulses per revolution with the dual element providing 120 pulses per revolution, with all other series providing 50 & 100 pulses respectively. Higher resolution is especially beneficial for slow speed applications, where more information is needed for smooth and accurate control. The dual sensor option also provides a direction signal allowing end-users to monitor the direction of shaft rotation .

Unlike competitive designs that breach the high pressure area of the motor to add the sensor, the Danfoss speed sensor option utilizes an add-on flange to locate all sensor components outside the high pressure operating environment. This eliminates the potential leak point common to competitive designs. Many improvements were made to the sensor flange including changing the material from cast iron to acetal resin, incorporating a Buna-N shaft seal internal to the flange, and providing a grease zerk, which allows the user to fill the sensor cavity with grease. These improvements enable the flange to withstand the rigors of harsh environments.

Another important feature of the new sensor flange is that it is self-centering, which allows it to remain concentric to the magnet rotor. This produces a consistent mounting location for the new sensor module, eliminating the need to adjust

the air gap between the sensor and magnet rotor. The o- ring sealed sensor module attaches to the sensor flange with two small screws, allowing the sensor to be serviced or upgraded in the field in under one minute. This feature is especially valuable for mobile applications where machine downtime is costly. The sensor may also be serviced without exposing the hydraulic circuit to the atmosphere. Another advantage of the self-centering flange is that it allows users to rotate the sensor to a location best suited to their application. This feature is not available on competitive designs, which fix the sensor in one location in relationship to the motor mounting flange.

FEATURES / BENEFITS	SENSOR OPTIONS
• Grease fitting allows sensor cavity to be filled with	Z - 4-pin M12 male connector
grease for additional protection.	This option has 50 pulses per revolution on all series except
	the DT which has 60 pulses per revolution. This option will
• Internal extruder seal protects against environmental	not detect direction.
elements.	Y - 3-pin male weatherpack connector*

•M12 or weatherpack connectors provide installation This option has 50 pulses per revolution on all series except

flexibility.	the DT which has 60 pulses per revolution. This option will
	not detect direction.

•Dual element sensor provides up to 120 pulses per

revolution and directional sensing.	X - 4-pin M12 male connector
	This option has 100 pulses per revolution on all series

•Modular sensor allows quick and easy servicing. except the DT which has 120 pulses per revolution. This

option will detect direction.

•Acetal resin flange is resistant to moisture, chemi-

cals, oils, solvents and greases.	W - 4-pin male weatherpack connector*
	This option has 100 pulses per revolution on all series

•Self-centering design eliminates need to set magnetexcept the DT which has 120 pulses per revolution. This

to-sensor air gap.	option will detect direction.
• Protection circuitry	*These options include a 610mm [2 ft] cable.

12 | © Danfoss | May 2018

BC267979667405en-000101