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RE
User guide
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Danfoss RE User guide

Technical Information
Orbital Motors
Type RE
powersolutions.danfoss.com
2 | © Danfoss | May 2018 BC267979667405en-000101
TABLE OF CONTENTS
TECHNICAL INFORMATION
Product Testing (Understanding the Performance Charts) .............................................................................................. 6
Shaft Nut Dimensions & Torque Specications ..............................................................................................................11
OPTIONAL MOTOR FEATURES
Speed Sensor Options ............................................................................................................................................. 12-13
Internal Drain ................................................................................................................................................................. 14
MEDIUM DUTY HYDRAULIC MOTORS
RE Product Line Introduction......................................................................................................................................... 16
BC267979667405en-000101 | 3© Danfoss | May 2018
OPERATING RECOMMENDATIONS
OIL TYPE
Hydraulic oils with anti-wear, anti-foam and demulsiers
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 signicantly shortened. Before using any type of uid, consult the uid
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 oper-
ating specications be taken into account when choosing a uid 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 uid performance.
congured 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.
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 ange 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, pul-
leys, sprockets and couplings must be properly aligned to
avoid inducing excessive thrust or radial loads. Although
the output device must t 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 ttings. 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 pre-
cautions 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
Caution! - Because it is possible for some large displace-
ment 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. A simple 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 ll brake release cavity and hoses
before all connections are tightened. To facilitate this op-
eration, all motor/brakes feature two release ports. One or both of these ports may be used to release the brake in the
4 | © Danfoss | May 2018 BC267979667405en-000101
OPERATING RECOMMENDATIONS & MOTOR CONNECTIONS
SERIES CIRCUIT
SERIES CIRCUIT
TYPICAL MOTOR/BRAKE SCHEMATIC
MOTOR/BRAKE PRECAUTION (continued)
unit. Motor/brakes should be congured so that the release
ports are near the top of the unit in the installed position.
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 ow 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 rst 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.
Once all system connections are made, one release port
must be opened to atmosphere and the brake release line carefully charged with uid 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.
NOTE: It is vital that all operating recommendations be followed. Failure to do so could result in injury or death.
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 ow 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 ow will go to that one motor. The others will not turn. If this condition can occur, a ow divider is
recommended to distribute the oil and act as a differential.
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.
BC267979667405en-000101 | 5© Danfoss | May 2018
PRODUCT TESTING
Max.
Max.
Theoretical rpm
Displacement tested at 54°C [129°F] with an oil viscosity of 46cSt [213 SUS]
Performance testing is the critical measure of a motor’s ability to convert ow and pressure into speed and torque. All
test stand calibration and stabilization of uid 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.]
2 [0.5]
4 [1]
8 [2]
Flow - lpm [gpm]
15 [4]
23 [6]
30 [8]
1
38 [10]
45 [12]
53 [14]
Cont.
61 [16]
64 [17]
Inter.
Pressure - bars [psi]
17 [250] 35 [500] 69 [1000] 104 [1500] 138 [2000] 173 [2500] 207 [3000] 242 [3500]
Torque - Nm [lb-in], Speed rpm
6
[127]
14
25
[140]
16
50
[139]
16
100
[127]
14
200
[113]
13
301
[91]
10
401
Overall Efficiency -
Theoretical Torque - Nm [lb-in]
21 [183] 41 [366] 83 [732] 124 [1099] 166 [1465] 207 [1831] 248 [2197] 290 [2564]
30
32
32
31
30
27
24
20
14
24
50
100
200
300
400
502
602
690
[262]
[286]
[280]
[275]
[262]
[243]
[212]
[177]
[127]
61
63
64
65
63
61
58
54
50
70 - 100%
21
43
99
199
297
398
500
601
689
[543]
[559]
[563]
[572]
[557]
[536]
[511]
[482]
[445]
7
[806]
91
18
[839]
95
43
[857]
97
92
[872]
99
191
[853]
96
295
[826]
93
390
[790]
89
499
[767]
87
600
[741]
84
688
5
40 - 69%
2
Intermittent Ratings - 10% of Operation
[1062]
120
124
129
131
130
127
123
120
124
17
[1099]
34
[1139]
87
[1155]
181
[1149]
284
[1125]
384
[1087]
498
[1060]
597
[1098]
658
0 - 39%
145
151
157
160
160
159
156
164
155
[1285]
11
[1340]
32
[1390]
79
[1420]
174
[1420]
271
[1409]
372
[1379]
485
[1451]
540
[1369]
644
169
178
187
186
186
187
185
193
185
8
[1496]
11
[1579]
32
[1652]
78
[1643]
160
[1646]
253
[1654]
346
[1638]
443
[1711]
526
[1640]
631
Max. Inter.Max. Cont.
191
203
211
216
218
3
220
213
228
217
[1693]
9
[1796]
31
[1865]
77
[1911]
154
[1930]
245
[1945]
339
[1883]
433
[2021]
510
[1918]
613
26
51
101
201
302
402
4
503
603
704
804
904
Flow represents the amount of uid passing through
1. the motor during each minute of the test.
Performance numbers represent the actual torque
6. and speed generated by the motor based on the cor-
responding input pressure and ow. The numbers on
Pressure refers to the measured pressure differential
2. between the inlet and return ports of the motor during the test.
The maximum continuous pressure rating and maxi-
3. mum intermittent pressure rating of the motor are
the top row indicate torque as measured in Nm [lb-in], while the bottom number represents the speed of the output shaft.
Areas within the white shading represent maximum
7.
motor efciencies.
separated by the dark lines on the chart.
Theoretical Torque represents the torque that the motor
8.
Theoretical RPM represents the RPM that the motor
4.
would produce if it were 100% volumetrically efcient.
Measured RPM divided by the theoretical RPM give the
would produce if it were 100% mechanically efcient.
Actual torque divided by the theoretical torque gives the
actual mechanical efciency of the motor.
actual volumetric efciency of the motor.
The maximum continuous ow rating and maximum
5.
intermittent ow rating of the motor are separated by the dark line on the chart.
6 | © Danfoss | May 2018 BC267979667405en-000101
ALLOWABLE BEARING & SHAFT LOADING
-100 -50 -25 0255075 100 mm-75
-100 -50 -25 0255075 100 mm-75
This catalog provides curves showing allowable radial loads at points along the longitudinal axis of the motor. They are
dimensioned from the mounting ange. Two capacity curves for the shaft and bearings are shown. A vertical 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 ange 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 interna-
9000
4000
tional 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 bear-
ings, removing any manufacturers specic safety factors or empirical data that inuences the ratings.
Manufacturers’ ratings are adjusted by diverse and system-
atic laboratory investigations, checked constantly with feed­back from practical experience. Factors taken into account
that affect bearing life are material, lubrication, cleanliness
8000
7000
6000
5000
4000
3000
2000
445 daN [1000 lb]
445 daN [1000 lb]
SHAFT
3500
3000
2500
2000
1500
1000
of the lubrication, speed, temperature, magnitude of the load and the bearing type.
1000
lb
BEARING
500 daN
The operating life of a bearing is the actual life achieved
by the bearing and can be signicantly 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
Bearing Life L10 = (C/P)p [106 revolutions]
L
= nominal rating life
10
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
BC267979667405en-000101 | 7© Danfoss | May 2018
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
RPM =
2.65 x KPH x G rm
RPM =
168 x MPH x G
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 = = 52.5
168 x 5 x 1
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 = x R (lb or N)
GVW
1000
Where:
GVW = gross (loaded) vehicle weight (lb or kg)
R = surface friction (value from Table 1)
Example
1500
RR = x 22 lbs = 33 lbs
1000
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 = x GVW (lb or N)
% Grade
100
Example
8 | © Danfoss | May 2018 BC267979667405en-000101
GR = x 1500 lbs = 300 lbs
20
100
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.
MPH x GVW (lb)
FA =
22 x t
KPH x GVW (N)
FA =
35.32 x t
Where: t = time to maximum speed (seconds)
Example FA = = 34 lbs
5 x 1500 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.
W x f x ri
TS =
G
(lb-in per motor)
W x f x rm
TS =
G
(N-m per motor)
Where:
f = coefcient of friction (see table 2)
W = loaded vehicle weight over driven wheel (lb or N)
Example TS = lb-in/motor = 4080 lbs
425 x .06 x 16
1
Table 2
Coefcient 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.
TE x ri
T = lb-in per motor
M x G
TE x rm
T = Nm per motor
M x G
Where: M = number of driving motors
Example T = lb-in/motor = 2936 lb-in
367 x 16
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 sufcient
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 = W
Example RL =
T
2
+ ( ) lb
ri
2
RL = W
425
2
2936
2
+ ( )
16
+ ( ) kg
2
T rm
2
= 463 lbs
Once the maximum motor RPM, maximum torque requirement, and the maximum load each motor must
support have been determined, these gures may then
be compared to the motor performance charts and to the bearing load curves to choose a series and displacement
to fulll the motor requirements for the application.
BC267979667405en-000101 | 9© Danfoss | May 2018
INDUCED SIDE LOAD
Distance
Side Load =
Side Load = 14855 Nm [3333 lbs]
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 sufcient bearing
and shaft capacity for the application.
Radius 76 mm [3.00 in]
Torque 1129 Nm [10000 lb-in]
HYDRAULIC EQUATIONS
Multiplication Factor
12
10
9
10
6
10
3
10
2
10
1
10
-1
10
-2
10
-3
10
-6
10
-9
10
-12
10
-15
10
-18
10
Theo. Speed (RPM) =
Abbrev. Prex
T tera G giga M mega
K kilo
h hecto
da deka
d deci
c centi m milli
u micro
n nano
p pico
f femto
a atto
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 pul-
ley/sprocket centerline to the mounting ange of the motor must also be determined. These two gures 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.
Torque Radius
1000 x LPM
Displacement (cm
3
/rev)
Theo. Torque (lb-in) =
Bar x Disp. (cm3/rev)
20 pi
Power In (HP) =
Bar x LPM
600
Power Out (HP) =
Torque (Nm) x RPM
9543
or
PSI x Displacement (in3/rev)
or
or
or
231 x GPM
Displacement (in3/rev)
6.28
PSI x GPM
1714
Torque (lb-in) x RPM
63024
10 | © Danfoss | May 2018 BC267979667405en-000101
35MM TAPERED SHAFTS
M24 x 1.5
1” T
3/4-28
1-1/4” T
1-20
1-3/8” & 1-1/2” T
1 1/8-18
To
To
12 [.47]
To
14 [.55]
To
15 [.61]
SHAFT NUT INFORMATION
Thread
A Slotted Nut
36 [1.42]
rque Specifications: 32.5 daNm [240 ft.lb.]
APERED SHAFTS
Thread
A Slotted Nut
42 [1.64]
6 [.22]
6 [.24]
15 [.59]
B Lock Nut
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 sufcient thickness must fully engage the
taper length of the shaft.
C Solid Nut
incorrect
correct
rque Specifications: 20 - 23 daNm [150 - 170 ft.lb.]
A Slotted Nut
rque Specifications: 38 daNm [280 ft.lb.] Max.
A Slotted Nut
33 [1.29]
APERED SHAFTS
Thread
44 [1.73]
APERED SHAFTS
Thread
48 [1.90]
5 [.19]
5 [.19]
5 [.19]
6 [.24]
12 [.48]
29 [1.13]28 [1.12]
Torque Specifications: 24 - 27 daNm [180 - 200 ft.lb.]
23 [.92]
33 [1.29]
24 [.95]
B Lock Nut
6 [.25]
14 [.55]
35 [1.38]38 [1.48]
Torque Specifications: 33 - 42 daNm [240 - 310 ft.lb.]
29 [1.14]
40 [1.57]
30 [1.18]
B Lock Nut
6 [.22]
35 [1.38]
51 [2.00]
36 [1.42]
16 [.63]
28 [1.10]
3.5 [.14]
16 [.63]
34 [1.34]
4 [.16]
16 [.63]
44 [1.73]
33 [1.28]
28 [1.11]
Torque Specifications: 20 - 23 daNm [150 - 170 ft.lb.]
C Solid Nut
44 [1.73]
38 [1.48]
Torque Specifications: 38 daNm [280 ft.lb.] Max.
C Solid Nut
48 [1.90]
15 [.61]
rque Specifications: 41 - 54 daNm [300 - 400 ft.lb.]
44 [1.73]42 [1.66]
Torque Specifications: 34 - 48 daNm [250 - 350 ft.lb.]
4 [.16]
42 [1.66]
Torque Specifications: 41 - 54 daNm [300 - 400 ft.lb.]
BC267979667405en-000101 | 11© Danfoss | May 2018
SPEED SENSORS
Danfoss offers both single and dual element speed sensor options providing a number of benets 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 benecial 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 ange to locate all sensor
components outside the high pressure operating environ-
ment. This eliminates the potential leak point common to
competitive designs. Many improvements were made to
the sensor ange including changing the material from
cast iron to acetal resin, incorporating a Buna-N shaft seal
internal to the ange, and providing a grease zerk, which allows the user to ll the sensor cavity with grease. These improvements enable the ange to withstand the rigors of
harsh environments.
Another important feature of the new sensor ange 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 ange
with two small screws, allowing the sensor to be serviced
or upgraded in the eld 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 ange 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 x the sensor in one location in relationship to the motor mounting ange.
FEATURES / BENEFITS
Grease tting allows sensor cavity to be lled with
• grease for additional protection.
Internal extruder seal protects against environmental
• elements.
M12 or weatherpack connectors provide installation
•
exibility.
Dual element sensor provides up to 120 pulses per
• revolution and directional sensing.
Modular sensor allows quick and easy servicing.
•
Acetal resin ange is resistant to moisture, chemi-
• cals, oils, solvents and greases.
Self-centering design eliminates need to set magnet-
• to-sensor air gap.
Protection circuitry
•
SENSOR OPTIONS
Z - 4-pin M12 male connector
This option has 50 pulses per revolution on all series except the DT which has 60 pulses per revolution. This option will not detect direction.
Y - 3-pin male weatherpack connector*
This option has 50 pulses per revolution on all series except the DT which has 60 pulses per revolution. This option will not detect direction.
X - 4-pin M12 male connector
This option has 100 pulses per revolution on all series except the DT which has 120 pulses per revolution. This option will detect direction.
W - 4-pin male weatherpack connector*
This option has 100 pulses per revolution on all series except the DT which has 120 pulses per revolution. This option will detect direction.
*These options include a 610mm [2 ft] cable.
12 | © Danfoss | May 2018 BC267979667405en-000101
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