Takeuchi Hydraulic excavator TB1140 (Serial No. 514400002~). Operator's Manual

SERVICE DATA

PERFORMANCE CRITERIA

Lever play

• Measure any discernible play at the tip of the lever or

pedal.

Backlash

• Measuring attitude: Completely retract the arm cylin-

der, and fully extend the bucket cylinder.

• Move the tips of the bucket teeth from side to side (left

and right), and measure the amount of play.

Slew bearing play

1. With the bucket in a no-load state, completely retract

the arm cylinder, fully extend the bucket cylinder,

move the dozer blade back, and make adjustments

so that the boom foot pin and bucket pin are at the

same height.

2. Attach a dial gauge to the bottom face of the slew

bearing’s outer race located near the front of the ex-

cavator, and set the dial gauge to 0.

3. Lower the boom, raise the crawler to the height, H,

and then read the dial gauge to get the measure-

ment.

Track tension

• Measuring attitude: Excavator body to be raised using

both the hoe attachment and the dozer blade. For

models with rubber crawlers, line up the crawler seam

joint (marked with an M or symbol) with the upper cen-

ter of the upper structure.

• Measure the width of the gap between the bottom sur-

face of the frame and the top surface of the track shoe

at the center of the crawler frame.

PERFORMANCE CRITERIA

2D0AS00

SERVICE DATA

TIGHTENING TORQUE

Hydraulic hose

UNION NUT

Tightening torque

ÜBERWURFMUTTER

ECROU D'UNION

Hose fitting size

Union nut (G)

Taper thread (R)

N·m

ft.-lb

N·m

ft.-lb

+4.9

+3.5

1/8

9.8

7.3

11.8 ± 1.2

8.7 ± 0.8

TAPER THREAD

KEGELWINDUNG

+4.9

+3.5

FILETAGE CONIQUE

1/4

24.5

18.1

29.4 ± 2.9

21.7 ± 2.1

+4.9

+3.5

3/8

49.0

36.2

53.9 ± 5.4

39.8 ± 3.9

58.8

+4.9

43.4

+3.5

1/2

88.3 ± 8.8

65.1 ± 6.4

+4.9

+3.5

2EAA01Z

3/4

117.7

86.8

147.1 ± 14.7

108.5 ± 10.7

137.3

+4.9

101.3

+3.5

196.1 ± 19.6

144.7 ± 14.3

Bite-type pipe fitting for steel pipe

Outer diameter of pipe

Tightening torque

(mm)

N·m

ft.-lb

34.3 ± 4.9

23.5 ± 3.5

41.7 ± 2.5

30.7 ± 1.7

58.8 ± 4.9

43.4 ± 3.5

88.3 ± 4.9

65.1 ± 3.5

93.2 ± 4.9

68.7 ± 3.5

132.4 ± 4.9

97.6 ± 3.5

2EAA02Z

205.9 ± 9.8

151.8 ± 7.2

27.2

245.2 ± 9.8

181.0 ± 7.2

313.8 ± 19.6

231.4 ± 14.3

313.8 ± 19.6

231.4 ± 14.3

411.9 ± 19.6

303.7 ± 14.3

TIGHTENING TORQUE

2E0AS00

SERVICE DATA

TIGHTENING TORQUE

Joint for piping

Tightening torque

Nominal thread

Steel

Cast steel

diameter (R)

N·m

ft.-lb

N·m

ft.-lb

1/8

11.8 ± 1.2

8.7 ± 0.8

10.8 ± 1.1

8.0 ± 0.7

1/4

29.4 ± 2.9

21.7 ± 2.1

24.5 ± 2.5

18.1 ± 1.7

3/8

53.9 ± 5.4

39.8 ± 3.9

49.0 ± 4.9

36.2 ± 3.5

1/2

88.3 ± 8.8

65.1 ± 6.4

73.5 ± 7.4

54.3 ± 5.3

3/4

147.1 ± 14.7

108.5 ± 10.7

127.5 ± 12.7

94.1 ± 9.3

2EAA03Z

196.1 ± 19.2

144.7 ± 14.3

171.6 ± 17.2

126.6 ± 12.5

Joint for piping (O-ring seal type)

O-RING

Nominal thread diameter

Tightening torque

O-RING

JOINT TORIQUE

(G)

N·m

ft.-lb

1/8

19.6 ± 2.0

14.5 ± 1.4

1/4

34.3 ± 4.9

25.3 ± 3.5

3/8

53.9 ± 4.9

39.8 ± 3.5

1/2

63.7 ± 4.9

47.0 ± 3.5

3/4

93.2 ± 4.9

68.7 ± 3.5

107.9 ± 9.8

79.5 ± 7.2

1-1/4

117.7 ± 9.8

86.8 ± 7.2

2EAA04Z

1-1/2

137.3 ± 9.8

101.2 ± 7.2

Nominal thread diameter

Tightening torque

(UNF)

N·m

ft.-lb

7/19-20

16.7 ± 2.0

12.3 ± 1.4

1/2-20

22.6 ± 2.0

16.6 ± 1.4

9/16-18

31.4 ± 2.9

23.1 ± 2.1

3/4-16

59.8 ± 4.9

44.1 ± 3.5

1-1/16-12

102.0 ± 5.9

75.2 ± 4.4

1-5/16-12

135.3 ± 7.8

99.8 ± 5.8

1-5/8-20

181.4 ± 9.8

133.8 ± 7.2

TIGHTENING TORQUE

2E0AS00

SERVICE DATA

TIGHTENING TORQUE

Bolts and nuts (JIS strength category 10.9)

Tightening torque

Thread

Size × pitch

General tightening points

Special tightening points

N·m

ft.-lb

N·m

ft.-lb

M6 × 1.0

9.8 ± 0.5

7.2 ± 0.4

11.8 ± 1.1

8.7± 0.4

M8 × 1.25

22.6 ± 1.1

16.6 ± 0.8

26.5 ± 2.5

19.5 ± 0.9

M10 × 1.5

47.1 ± 2.4

34.7 ± 1.7

54.9 ± 4.9

40.5 ± 2.0

Coarse

M12 × 1.75

83.4 ± 4.1

61.5 ± 3.0

97.1 ± 7.4

71.6 ± 3.5

M14 × 2.0

134.4 ± 6.7

99.1 ± 4.9

155.9 ± 12.7

115.0 ± 5.7

M16 × 2.0

207.9 ± 10.4

153.3 ± 7.7

241.2 ± 17.2

177.9 ± 8.9

M20 × 2.5

410.9 ± 20.5

303.1 ± 15.1

475.6 ± 23.7

350.8 ± 17.5

M8 × 1.0

24.5 ± 1.2

18.1 ± 0.9

28.4 ± 1.4

21.0 ± 1.0

M10 × 1.25

50.0 ± 2.5

36.9 ± 1.8

58.8 ± 2.9

43.4 ± 2.2

M12 × 1.5

87.3 ± 4.3

64.4 ± 3.2

102.0 ± 5.1

75.2 ± 3.8

Fine

M14 × 1.5

135.3 ± 6.8

99.9 ± 5.0

157.9 ± 7.8

116.5 ± 5.8

M16 × 1.5

220.6 ± 11.0

162.7 ± 8.1

256.0 ± 12.7

188.8 ± 9.4

M20 × 1.5

452.1 ± 22.6

333.4 ± 16.6

524.7 ± 26.1

387.0 ± 19.2

1. General tightening points (non-lubricated)

All securing points that have no special tightening

torque specified in this manual and that are not spe-

cial tightening points.

2. Special tightening points (grease with molybdenum

disulfide applied)

Points where a specific tightening torque is specified

in this manual.

3. Points where thread-locking compound should be

applied (ThreeBond #1324).

4. If a tightening torque value is specified in this manual

for a point not listed in the table above, follow the

specification listed in the manual.

5. To tighten multiple bolts and nuts evenly, tighten op-

posite bolts/nuts alternately as a pair.

TIGHTENING TORQUE

2E0AS00

SERVICE DATA

TIGHTENING TORQUE

Hose clips

For the hydraulic hoses

Tightening

Part no.

Tightening range

torque

15337-*****

mm (in.)

N·m

ft.-lb

-00013

9.5 to 12 (0.37 to 0.47)

-00016

11 to 16 (0.43 to 0.63)

3.4

2.5

-00019

13 to 20 (0.51 to 0.79)

-00022

14 to 22 (0.55 to 0.87)

-00025

17 to 25 (0.67 to 0.98)

-00028

22 to 30 (0.87 to 1.18)

4.8

3.6

-00035

25 to 35 (0.98 to 1.38)

-00041

30 to 40 (1.18 to 1.57)

7 mm (0.28 in.)

-00048

35 to 50 (1.38 to 1.97)

Tightening range

-00054

40 to 55 (1.57 to 2.17)

5.8

4.3

-00060

45 to 60 (1.77 to 2.36)

-00070

55 to 70 (2.17 to 2.76)

-00080

60 to 80 (2.36 to 3.15)

-00090

70 to 90 (2.76 to 3.54)

6.7

5.0

-00102

80 to 100 (3.15 to 3.94)

-00115

90 to 120 (3.54 to 4.72)

TIGHTENING TORQUE

2E0AS00

SERVICE DATA

TIGHTENING TORQUE

For hoses other than the hydraulic hoses

Tightening

Part no.

Tightening range

torque

15337-

mm (in.)

N·m

ft.-lb

*****

-00015

8 to 15 (0.31 to 0.59)

2.5 to

1.8 to

-00017

11 to 17 (0.43 to 0.67)

3.4

2.5

-00021

13 to 22 (0.51 to 0.87)

-00024

15 to 25 (0.59 to 0.98)

-00029

19 to 29 (0.75 to 1.14)

3.9 to

2.9 to

-00031

19 to 31 (0.75 to 1.22)

4.9

3.6

-00033

22 to 33 (0.87 to 1.30)

-00039

26 to 39 (1.02 to 1.54)

7 mm (0.28 in.)

Tightening range

-00045

32 to 45 (1.26 to 1.77)

-00051

32 to 51 (1.26 to 2.01)

-00052

38 to 51 (1.50 to 2.01)

-00057

44 to 57 (1.73 to 2.24)

-00061

40 to 61 (1.57 to 2.40)

-00066

50 to 66 (1.97 to 2.60)

-00069

50 to 69 (1.97 to 2.72)

-00071

50 to 71 (1.97 to 2.80)

-00076

58 to 76 (2.28 to 2.99)

-00081

60 to 81 (2.36 to 3.19)

-00086

68 to 86 (2.68 to 3.39)

-00091

70 to 91 (2.76 to 3.58)

4.9 to

3.6 to

-00096

77 to 96 (3.03 to 3.78)

5.9

4.3

-00101

80 to 101 (3.15 to 3.98)

-00113

87 to 113 (3.43 to 4.45)

-00121

100 to 121 (3.94 to 4.76)

-00131

110 to 131 (4.33 to 5.16)

-00139

104 to 138 (4.09 to 5.43)

-00166

130 to 166 (5.12 to 6.54)

-00181

150 to 181 (5.91 to 7.13)

-00206

175 to 206 (6.89 to 8.11)

-00232

200 to 232 (7.87 to 9.13)

-00257

226 to 257 (8.90 to 10.12)

-00283

251 to 283 (9.88 to 11.14)

-00308

277 to 307 (10.91 to 12.09)

TIGHTENING TORQUE

2E0AS00

FUNCTION

HYDRAULIC PUMP (MAIN)

This pump is formed of two variable displacement piston

pumps (1) and (2) and a gear pump (3). The two variable

displacement piston pumps operate over the same shaft.

However, the gear pump (3) operates on a different shaft

than the variable displacement piston pumps.

Roughly speaking, this pump is formed of a cylinder

block (4) that produces rotating motion, a regulator (5)

that changes the discharge flow rate, and a PTO group

(6) that is used to transmit the gear pump motion to the

driving shaft.

Cylinder block

The cylinder block (4) is formed of pistons (7), and at its

end surface, it is in contact with the valve plate (10) that

contains the intake port (8) and the discharge port (9).

The cylinder block (4) rotates freely and is connected to

the shaft (11) via the spline. The swash plate (12), on the

other hand, is fixed at an angle to the housing, and the

pistons (7) are designed to rotate along with the swash

plate (12).

Here, the cylinder block (4) rotates as the shaft (11) is ro-

tated, and the pistons (7) mounted in the cylinder block

(4) follow and move back and forth with the motion of the

swash plate (12), which activates the suction and dis-

charge pumps.

In this way, the nine pistons (7) complete one stroke of in-

take and exhaust for every stroke of the cylinder block

(4). Thus, continuous operation of intake and exhaust

can be obtained by continuous rotation of the shaft (11).

The displacement of the pistons

(7) can be varied

through modification of the angle of inclination of the

swash plate (12) as the degree of displacement depends

on the inclination of the swash plate (12).

Regulator

This regulator is equipped with three control functions, a

flow rate control function for discharging only the neces-

sary amount according to the pilot pressure Pi from the

control valve, a function for controlling horsepower to

prevent excessive load on the motor using the discharge

pressures P1 and P2, and a power shift control function

for controlling the set pump horsepower setting using the

power shift pressure Pf from the Pr pump (2nd service

and blade). If these control functions are used together,

low-inclination operation commands (low flow rate com-

mands) are given priority based on mechanical calcula-

tions.

HYDRAULIC PUMP (MAIN)

3I0AS00

FUNCTION

HYDRAULIC PUMP (MAIN)

1. Flow rate control

The angle of inclination (discharge rate) of the swash

plate of the pump is controlled by the pilot pressure Pi

from the control valve.

This regulator uses a load flow rate control (negative con-

trol) method through which the discharge rate Q is low-

ered as the pilot pressure Pi is increased, such that when

a command is issued for the pilot pressure Pi according

to the amount of flow required for operation, the pump

discharges only the necessary amount so that no power

is wasted unnecessarily.

Decrease in flow rate

When the pilot pressure Pi from port Ps2 in the control

valve is increased, the piston (1) moves to the right side

and stopped at a position at which the force of the spring

(2) is balanced with the hydraulic pressure.

The pin (4) attached to the lever (3) is inserted into the

groove (A) on the piston (1), and when the piston (1)

moves, the lever (3) turns clockwise around the securing

pin (5) of the pivot point (B).

The pin (7) attached to the lever (6) is inserted into the

hole (C) on the lever (3), and the pin (7) moves right when

the lever (3) rotates clockwise. The pin (10) secured to

the inclined pin (9) used to tilt the swash plate (8) is at-

tached to the second surface (D) of the lever (6), and the

lever (6) turns counter-clockwise around the second sur-

face (D) when the pin (7) moves. The spool (11) is linked

to the lever (6) via the pin (12) and moves to the right.

When the spool (11) moves, the discharge pressure P1

is transmitted to the port Cl through the spool (11) and

flows to the large-diameter section of the servo piston

(13). The discharge pressure P1 normally flows to the

small-diameter section of the servo piston (13), but the

servo piston (13) moves to the right due to the differential

area, causing the angle of inclination to decrease, which

results in the discharge pressure P1 flowing into the

large-diameter section.

When the servo piston (13) moves to the right, the sec-

ond surface (D) also moves to the right. The spring (14)

is attached to the spool (11) that normally exerts a pulling

force on the spool (11) that pulls it to the left, which caus-

es the pin (7) to be pushed into the hole (C) of the lever

(3). As can be inferred from the above, the lever (6) turns

counter-clockwise around the hole (C) when the second

surface (D) moves, resulting in the spool (11) moving to

the left. The movement of these parts causes the opening

between the sleeve (15) and the spool (11) to gradually

close, and the servo piston (13) stops at the position at

which the opening is completely closed.

HYDRAULIC PUMP (MAIN)

3I0AS00

FUNCTION

HYDRAULIC PUMP (MAIN)

Increase in flow rate

When the pilot pressure Pi decreases, the piston (1)

moves to the left due to the force of the spring (2), and

the lever (3) turns clockwise around section B. The pin

(7) is pushed into the hole (C) on the lever (3) via the

spool (11), pin (12), and lever (6), which causes the lever

(6) to move counter-clockwise around the second width

(D) when the lever (3) moves clockwise, which results in

the spool (11) moving to the left.

When the spool (11) moves, port CI is connected to port

T, the pressure on the large-diameter section of the servo

piston (13) is released, and the servo piston (13) is

moved to the left by the discharge pressure P1 in the

small-diameter section, which causes the flow rate to in-

crease.

The second surface (D) moves to the left, causing the le-

ver (6) to turn clockwise around the hole (C), when the

servo piston (13) moves, resulting in the spool (11) mov-

ing to the right. The spool (11) continues to move until the

opening between the sleeve (15) and the spool (11) clos-

es and stops at the position at which the opening is

closed.

2. Horsepower control

As the discharge pressure P1 of the self-operating pump

and the discharge pressure P2 of the other pump in-

crease, the angle of inclination of the pump (discharge

rate) drops automatically such that the input torque is

controlled so as to be maintained below a set value. (The

input horsepower is constant when the rotation speed is

constant.)

With a tandem double pump, a simultaneous full-horse-

power method is used for operation according to the total

load pressure of the two pumps such that the regulators

in the two pumps are controlled and maintained at the

same angle of inclination (discharge rate) when horse-

power control is in effect. For this reason, when horse-

power control is in effect, engine overloading is prevent-

ed automatically independent of the load on the two

pumps.

HYDRAULIC PUMP (MAIN)

3I0AS00

FUNCTION

HYDRAULIC PUMP (MAIN)

Prevention of excessive load

When the discharge pressure P1 of the self-operating

pump or the discharge pressure P2 of the other pump in-

creases, P1 and P2 are exerted on the step section of the

piston (16), which causes the rod (17) to be pushed to

the right to the position at which the spring force and oil

pressure of the spring (18) and spring (19) are balanced.

The movement of the rod (17) is transmitted to the lever

(20) via the pin (4), which causes the lever (20) to move

counter-clockwise around the pivot point (E). The pin (7)

attached to the lever (6) is thrust into the hole (F) on the

lever (20), which causes the lever (6) to move clockwise

around the second surface (D) when the lever (20)

moves counter-clockwise, resulting in the spool (11)

moving to the right.

When the spool (11) moves, the discharge pressure P1

causes the discharge rate in the large-diameter section

of the piston (13) to drop via port Cl, which works to pre-

vent excess load on the motor.

The movement of the servo piston (13) is transmitted to

the lever (6) via the second surface (D), which causes

the lever (6) to move counter-clockwise around the hole

(F), resulting in the spool (11) moving until the opening

between the spool (11) and the sleeve (15) and stopping

at the position at which the opening is closed.

Restoration of flow rate

When the discharge pressure P1 of the self-operating

pump or the discharge pressure P2 of the other pump

decreases, the rod (17) is pushed back by the spring

(18) and spring (19), and the lever (20) rotates clockwise

around the pivot point (E). The lever (6) turns counter-

clockwise around the second surface (D) when the lever

(20) turns clockwise, resulting in the spool (11) moving to

the left. As can be inferred from the above, port Cl opens

into the tank port, causing the pressure in the large-diam-

eter section of the servo piston (13) to be released, re-

sulting in the servo piston (13) moving to the left and the

pump discharge rate increasing.

The movement of the servo piston (13) is transmitted to

the spool (11) via the mechanism in the lever (6), and the

spool (11) continues to move until the opening between

the spool (11) and the sleeve (15) is closed.

HYDRAULIC PUMP (MAIN)

3I0AS00

FUNCTION

HYDRAULIC PUMP (MAIN)

3. Power shift (Lowered horsepower control)

The pressure from the Pr pump (2nd service and blade)

controls the set pump horsepower as a power shift pres-

sure Pf.

When the power shift pressure Pf is increased, the rod

(17) moves to the right via the pin (21) and piston (16),

which causes the angle of inclination of the pump to

drop and the set horsepower to decrease, as was de-

scribed in the explanation for operation to prevent ex-

cessive load for control of horsepower. Conversely, if

the power shift pressure Pf is decreased, the set

horsepower will increase.

4. Command override system for low-inclination (low flow

rate) operation

As described above, the inclination command for flow

rate and horsepower control is transmitted to the lever (6)

and spool (11) via the holes (C) and (F) in the lever (3)

and lever (20). In the diagram shown at right, the lever (3)

is being affected by a command that causes its angle of

inclination to be greater than that of the lever (20) such

that the pin (7) makes contact with only the hole (F) in the

lever (20), which has the smaller angle of inclination. As

a result, the hole (C) of the lever (3) remains open and

free of contact with the pin (7).

With this kind of mechanical selection system, low-incli-

nation commands for flow rate control and horsepower

control are given priority over other commands.

HYDRAULIC PUMP (MAIN)

3I0AS00

FUNCTION

HYDRAULIC PUMP (SUB)

The hydraulic pump (sub) (1) is a gear pump that is a

constant-volume pump that discharges a constant vol-

ume of discharge material over a constant speed.

The hydraulic pump (sub) (1) is connected to the PTO

group (2) of the hydraulic pump (main) through gears

that transmit the rotation of the engine from the PTO

group.

Hydraulic pump, PTO group

The gear pump is composed of two mutually engaging

gears (drive gear (6) and driven gear (7)) that are con-

tained in a gear case. When the drive gear (6) is rotated,

the space between the case and the gears is filled with

the oil that flows from the inlet to the outlet.

3I1AQ02Z

HYDRAULIC PUMP (SUB)

3I1AS00

FUNCTION

CONTROL VALVE

When all spools are in the neutral position

Neutral passage (Fig. 1), (Fig. 2)

Fig. 2

The oil supplied from the port P1 is sent from the neutral passage (L1) to the neutral passage (L2) and through the

opening (Lc1) in the low-pressure relief valve into the tank passage (Ta) to be returned to ports T1 and T2.

The oil supplied from the port P2 is sent from the neutral passage (R1) to the oil passage (R2) via the neutral cut spool

and through the opening (Rc1) in the low-pressure relief into the tank passage (Ta) to be returned to ports T1 and T2.

The pressure in the pressure chambers (L2) and (R2) of the upstream flow section of the low-pressure relief vale flows

into the pumps from ports ps1 and ps2 to control the discharge rates of pumps P1 and P2.

If an excessive amount of oil flows into the neutral passages, the low-pressure relief valve operates to prevent the pres-

sure in ports ps1 and ps2 from rising to an abnormal level.

Fig. 1

In addition, the oil supplied from the port P1 flows from the passage (2) into the parallel passage (L3) via the bridge (4)

and straight travel valve and through the passage (1). The auxiliary, slew, boom 2, and arm 1 sections are connected

together via each check valve, and the flow is stopped by the spool in each section.

Fig. 2

The parallel passage (L3) is connected to the neutral passage (L1) via the passage (S1-2) and the check valve (S1-1)

such that the oil flows from port P1 to the parallel passage (L3) without going through the straight travel valve when the

travel section (Section 1) is not operating.

Fig. 1

The oil (3rd pump) supplied from port Pr flows from the passage (13) in the inlet section into the neutral passage (Pg).

The oil that flows into the blade section flows from the passage (Tg) into the inlet section via the outlet section (cover)

and flows into the oil in the machine body tank passage (Ta).

Fig.2

In addition, the flow of the oil supplied from the port Pr is connected to the blade section via the parallel passage (G3)

and check valve and is stopped by the spool.

Signal passage (Fig. 1)

The oil supplied from the port PP flows to port PT via the opening (Lc3). At the same time, it also flows from the land

(Rc3) through the land (Lc4) and passage (6) and into the drain passage (DR).

Part of the oil supplied from the port PP flows to port PA from the opening (Lc5). In addition, it also flows from the bucket

spool land (Rc4) and into the drain passage (DR) via the passages (L4), (9), and (R4).

The oil that passes through the opening (Lc6) flows into the tank passage (Ta) from the land (Lc7). The oil also flows

from the travel spool land (Rc5) and into the tank passage (Ta) through the passage (5).

At this time, the oil that flows through the passage (5) flows into the switching pressure chamber (Pts) from the spool

cycle passage of the straight travel valve.

The chamber (Tts) on the opposite side from the straight travel valve spool is connected to the tank passage (Ta) via

a notch opening in the outer circumference of the spool and used to decrease the impact of shocks during switching.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Independent operation

Travel spool switching (Fig. 3), (Fig. 4)

5 Travel (R)

f Neutral

d Travel (L)

g Switching

e Straight travel

When the pressure from the pilot port pb1 (pa1) of the travel (R) section (section 1) increases causing the travel spool

to be switched, the oil supplied from the port P1 flows from the neutral passage (L1) through the spool neck and into

the port B1 (A1). The oil that returns back returns to the tank passage (Ta) from port A1 (B1) through the spool neck.

When the pressure from the pilot port pb6 (pa6) of the travel (L) section (section 6) increases causing the travel spool

to be switched, the oil supplied from the port P2 flows from the neutral passage (R1) through the spool neck or the

passage (S6-1) and into the port B6 (A6).

At this time, the poppet (S6-2) does not open as the pressure in the parallel passage (R3) is the same as that in the

passage (S6-1).

The oil that returns back returns to the tank passage (Ta) from port A6 (B6) through the spool neck.

Either the land (Lc4) or the land (Rc3) closes when the spool in either travel section (Section 1 or Section 6) switches.

The flow of the oil supplied from the port PP into the tank passage is blocked, which causes the pressure in the port

PT to increase.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

1st auxiliary line spool switching (Fig. 5)

4 1st auxiliary line

d Travel (L)

The neutral passage (L1) closes when the pressure from the pilot port pb2 (pa2) of the 1st auxiliary line (Section 2) is

increased causing the spool to switch. The oil supplied from the port P1 flows from the parallel passage (L3) and into

port B2 (A2) through the load check valve (S2-1), passage (S2-2), and spool neck.

The oil that returns back returns to the tank passage (Ta) from port A2 (B2) through the spool neck.

A load check is used in this section that allows external oil to flow from port P4.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

3 Slew

c Bucket

Slew spool switching (Fig. 6)

The neutral passage (L1) closes when the pressure in the pilot port Pb3 (Pa3) in the slew section (Section 3) increases

and causes the slew spool to switch. The oil supplied from the port P1 flows from the parallel passage (L3) through the

load check valve (S3-1), passage (S3-2), and spool neck and into the passage B3 (A3).

The oil that returns back returns from port A3 (B3) through the spool neck to the tank passage (Ta).

Bucket spool switching (Fig. 6)

The neutral passage (R1) closes when the pressure in the pilot port pb7 (pa7) in the bucket section (Section 7) increas-

es and causes the bucket spool to switch. The oil supplied from port P2 flows from the parallel passage (R3) and into

port B7 (A7) through the load check valve (S7-1), passage (S7-2), and spool neck.

The oil that returns back returns from port A7 (B7) through the spool neck to the tank passage (Ta).

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Raising (2nd-speed flow) (Fig. 8)

2 Boom 2

b Boom 1

The neutral passage (R1) closes when the pressure in the pilot port pa8 in the boom 1 section (Section 8) increases

and causes the boom 1 spool to switch. The oil supplied from the port P2 flows through the parallel passage (R3), load

check valve (S8-1), and spool neck to the port A8.

The neutral passage (L1) closes when the pressure in the pilot port pa4 in the boom 2 section (Section 4) increases

and causes the boom 2 spool to switch. The oil supplied from the port P1 flows through the parallel passage (L3), load

check valve (S4-1), spool neck, and passage (7) to the port A8. The oil that returns back returns from port B8 through

the spool neck to the tank passage (Ta).

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Lowering (Reclaiming) (Fig. 9)

2 Boom 2

b Boom 1

The neutral passage (R1) closes when the pressure in the pilot port pb8 in the boom 1 section (Section 8) increases

and causes the boom 1 spool to switch. The oil supplied from the port P2 flows through the parallel passage (R3), load

check valve (S8-1), and spool neck to the port B8. Simultaneously, when the pressure in the port pc2 increases causing

the poppet (AD3) of the anti-drift valve to switch and the pressure in the spring chamber (AD5) to drop, the poppet

(AD1) opens, and oil returning from the port A8 flows into the tank passage (Ta). Part of the oil returning back pushes

on and opens the poppet (S8-3) inside the boom 1 spool, and flows through the passage (S8-2) into the port B8 to

prevent cavitation from forming on the cylinder load side.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Arm spool switching

Dumping (2nd-speed flow) (Fig. 10)

1 Arm 1

a Arm 2

When the pressure in the pilot port pb5 of the arm 1 section (Section 5) increases causing the arm 1 spool to switch,

the oil supplied from the port P1 flows from the neutral passage (L1) through the load check valve (S5-1), passage (S5-

2), and spool neck and into the port A5.

When the pressure in the pilot port pa9 of the arm 2 section (Section 9) increases causing the arm 2 spool to switch,

the oil supplied from the port P2 flows from the neutral passage (R1) through the load check valve (S9-1), passage (S9-

2), spool neck, and passage (10) and into the port A5. Simultaneously, part of the oil supplied from the port P2 flows

from the opening (S9-3) in the passage (R3) through the check valve (S9-4), passage (S9-2), and passage (10) and

into the port A5. The oil that returns back returns from the port B5 through the arm 1 spool neck back into the tank

passage (Ta), and the oil from the passage (11) returns through the arm 2 spool neck back into the tank passage (Ta).

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Crowding (2nd-speed flow) (Fig. 11), (Fig. 12)

1 Arm 1

a Arm 2

When the pressure in the pilot port pb5 of the arm 1 section (Section 5) increases causing the arm 1 spool to switch,

the oil supplied from the port P1 flows from the neutral passage (L1) through the load check valve (S5-1), passage (S5-

2), and spool neck and into the port B5.

When the pressure in the pilot port pb9 of the arm 2 section (Section 9) increases causing the arm 2 spool to switch,

the oil supplied from the port P2 flows from the neutral passage (R1) through the load check valve (S9-1), passage (S9-

2), spool neck, and passage (11) and into the port B5. Simultaneously, part of the oil supplied from the port P2 flows

from the opening (S9-3) in the passage (R3) through the check valve (S9-4), passage (S9-2), and passage (11) and

into the port B5.

When the pressure in the port pc1 increases causing the poppet (AD3) of the anti-drift valve to switch and the pressure

in the spring chamber (AD5) to drop, the poppet (AD1) opens, and oil returning from the port A5 flows through the

spool neck, passage (S5-3), and arm variable reclaiming opening (Lc8) back into the tank passage (Ta). Part of the oil

returning back pushes on and opens the poppet (S5-4) inside the arm 1 spool, and flows through the passage (S5-2)

into the port B5 to increase the speed of the cylinder. This also works to prevent cavitation from forming on the bottom

side.

Variable reclaiming (during crowding) (Fig. 11), (Fig. 12)

During crowding of the arm, the spool (S5-6) moves in response to the pressure in the passage (S5-2) flowing from the

passage (S5-5), causing the degree to which the arm variable reclaiming opening (Lc8) is opened to change. If the

pressure in the passage (S5-2) is high, the amount that the spool (S5-6) moves increases causing the degree to which

the opening (Lc8) is opened to drop. This causes the reclaiming flow rate to change in response to the pressure at the

bottom of the am cylinder.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Parallel opening for the arm (Fig. 10), (Fig. 11), (Fig. 12,) (Fig. 13), (Fig. 14)

Fig. 10, Fig. 11

There are openings formed in both the arm 1 section (Section 5) and arm 2 section (Section 9) in the parallel circuit for

the arm for this valve that are used to control the flow rate so that the arm speed is at a proper speed even during

composite operation.

After the parallel circuit of the arm 2 section (Section 2) closes the opening (RC6) of the sleeve (S9-3) from the parallel

passage (R3), it is connected to the passage (S9-2) through the poppet (S9-4).

Fig. 13, Fig. 14

After the parallel circuit of the arm 1 section (Section 5) pushes open the poppet (S5-8) from the parallel passage (L3)

and the opening (Lc9) of the parallel variable opening spool closes, the passages (S5-2) and (12) are connected to-

gether.

The degree to which the opening (Lc9) is opened can be changed using increases in pressure in the pilot port (pbu)

(pc3).

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Relief valve

Main relief valve for the machine body (Fig. 17)

The oil supplied from the port P1 flows through the poppet (LP), or the oil supplied from the port P2 flows through the

poppet (RP) and passage (3), and into the main relief valve. When the main relief valve operates, the maximum pres-

sure of the pumps on the P1 and P2 sides is restricted to a set value.

Relief valve for the add-on Pr (Fig. 18)

The oil supplied from the port Pr flows into the main relief valve. The maximum pressure of the Pr pump is limited to a

set value through operation of the main relief valve.

Overload relief valve

An overload relief valve is provided in each of the cylinder ports in each section that prevents the pressure in the ac-

tuator from rising to an abnormal level due to an external force.

This relief valve is also equipped with a function designed to prevent suction of oil from the tank and cavitation from

occurring when the pressure in the cylinder port becomes a negative pressure.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Composite operation

Composite travel operation (Fig. 19), (Fig. 20)

During simultaneous left-and-right travel operation (during forward travel, reverse travel, or spin turns), when opera-

tions other than travel operations are run simultaneously, or when simultaneous left-and-right travel operations are run

while other operations other than travel operations are being run, the oil supplied from the port PP is blocked from flow-

ing to the tank passage (Ta) by signal land sections other than travel sections switched with the lands (Lc4), (Lc7),

(Rc3), and (Rc5), which causes the pressure in the signal passage to increase to the relief pressure setting for the hy-

draulic generator for signals.

The straight travel spool is switched by the increase in the signal pressure. The pressure in the ports PT and PA also

increases.

When the straight travel spool switches, the oil supplied from the port P1 flows from the neutral passage (L1) and into

the travel (R) section (Section 1), and at the same time, through the passage (2), straight travel spool neck, and neutral

passage (R1) and into the travel (L) section (Section 6).

The oil supplied from the port P2 flows through the straight travel spool neck and passage (1) and into the parallel pas-

sage (L3).

The travel sections (Section 1 and Section 6) are moved by the oil supplied from the port P1 and devices in other op-

erating sections are moved by the oil supplied from the port P2, which works to prevent veering in travel during com-

posite operations involving simultaneous left-and-right travel operation and operation of other devices.

If the load pressure in other sections is higher than the load pressure in the travel section (Section 6), part of the oil

supplied from the port P2 pushes on and opens the poppet (S6-2) and flows through the opening at the end of the

poppet and into the passage (S6-1). This works to alleviate the impact from shocks from deceleration with travel during

switching of the straight travel valve.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Anti-drift valve

The anti-drift valve is used to prevent spontaneous drop

of the arm (boom) cylinder and is mounted in the cylinder

port on the arm rod (boom bottom) side.

In neutral, the cylinder port pressure flows into the spring

chamber (AD5) from the passage (AD2) through the hol-

low hole in the poppet (AD3) and the passage (AD4).

The poppet (AD1) is firmly seated by the pressure differ-

ential produced by the spring force and differential area

of the poppet.

When the arm is in the dump position (the boom is

raised), the oil supplied from the pump pushes the pop-

pet (AD1) open and flows into the cylinder port.

When the arm is in the crowd position (the arm is low-

ered), the pc1 (pc2) pressure increases causing the

poppet (AD3) to switch, which leads to the oil in the

spring chamber (AD5) to flow through the hollow hole in

the poppet (AD3) and hollow hole in the spool (AD6) and

into the drain passage (DR). This causes the poppet

(AD1) to open, and the oil that returned from the cylinder

port flows into the tank passage (Ta) through the spool.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Main relief valve

The main relief valve is mounted between the pump cir-

cuit and tank circuit of each inlet housing and serves to

maintain the circuit pressure at the set value.

Machine body main relief valve

This relief valve is installed between the neutral passage

"LP"

“HP” and low-pressure passage “LP,” and oil flows

through the opening hole in the main poppet into the in-

ternal cavity (C) to fill the internal cavity (C).

In addition, the opening in the sleeve (2) and the main

"HP"

poppet (1) are firmly seated using the different areas of

“A” and “B.”

3J0AS20

When the pressure in the neutral passage “HP” reaches

the set pilot spring force, the pilot poppet (3) opens.

"LP"

The oil flows around the pilot poppet (3) from the hole (D)

and through the gap (E) into the tank passage “LP.”

"HP"

3J0AS21

When the pilot poppet (3) is opened, the pressure in the

internal cavity (C) drops causing the main poppet (1) to

"LP"

open, which results in the oil in “HP” flowing into the con-

necting passage “LP.”

"HP"

3J0AS22

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Add-on main relief valve

This relief valve is installed between the neutral passage

“HP” and low-pressure passage “HP,” and oil flows

"LP"

through the opening hole in the main poppet into the in-

ternal cavity (C) to fill the internal cavity (C).

In addition, the opening in the sleeve (2) and the main

poppet (1) are firmly seated using the different areas of

"HP"

“A” and “B.”

3J0AS23

When the pressure in the neutral passage “HP” reaches

the set pilot spring force, the pilot poppet (3) opens.

The oil flows around the pilot poppet (3) from the hole (D)

"LP"

and through the gap (E) into the tank passage “LP.”

"HP"

3J0AS24

When the pilot poppet (3) is opened, the pressure in the

internal cavity (C) drops causing the main poppet (1) to

open, which results in the oil in “HP” flowing into the con-

necting passage “LP.”

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Port relief valve

The port relief valve is located between the actuator and

the tank circuit. It protects the actuator from pressure

shock caused by the sudden blocking of the actuator

port or by overloading, or absorbs abnormal pressure

caused by an external force. In addition, it also prevents

the oil from forming suction cavitation in the tank when

the actuator port experiences a negative pressure.

This relief valve is installed between the cylinder port

“HP” and low-pressure passage “LP,” and oil flows

through the opening hole in the piston (C) to fill the inter-

nal cavity (G).

In addition, the sleeve (K) and the main poppet (D) are

firmly seated using the different areas of “A” and “B.”

When the pressure in the cylinder port “HP” reaches the

set spring force of the pilot poppet, the pilot poppet (E)

opens.

"LP"

E H

The oil flows around the circumference of the poppet and

through the hole (H) into the low-pressure passage “LP.”

"HP"

3J0AS27

When the pilot poppet (E) is opened, oil flows through the

opening (I) in the piston (C), which produces a pressure

differential with the passage “HP” on the back of the pis-

ton (C), causing the piston (C) to move and set the pop-

pet (E).

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

The oil flowing from the passage “HP” to the back of the

poppet (D) flows only through the gap between the pop-

pet (D) and piston (C) and the opening (F), which causes

the pressure differential to increase. This causes the

poppet (D) to open, resulting in oil flowing into the direct

passage “LP.”

An anti-boiled unit that supplies oil when cavitation forms

is mounted in the cylinder port “HP” in this relief valve.

The sleeve (K) opens due to the differential area between

“A” and “B” when the pressure of the cylinder port “HP”

from the low-pressure side “LP” is low.

The oil from the low-pressure side “LP” flows into the low-

pressure side of the cylinder port “HP,” which prevents

cavitation from forming.

CONTROL VALVE

3J0AS00

FUNCTION

CONTROL VALVE

Negative control valve

This valve supplies negative control signals to the vari-

able displacement hydraulic pumps.

The negative control signals maintain the angle of incli-

nation of the swashplate so that the discharge rate of the

pump is kept at the minimum rate when the engine is

stopped.

Generation of signal pressure

The oil supplied from the pump port (P1) flows through

the neutral passage (L1) and from the neutral down-

stream passage (A) through the negative control open-

ing (D) into the tank passage.

At this time, a pressure is generated in the passage (B)

by the negative control opening (D) that flows into the

negative control signal port (Ps1) from the passage (E).

When the main spool for upstream flow through the neu-

tral downstream passage (A) is operated, the oil flowing

through the neutral downstream passage (A) decreases

in volume, causing the negative control signal pressure

to become low.

Relief operation

If an excessive amount of oil flows into the neutral down-

stream passage (A), the pressure generated in the pas-

sage (B) by the negative control opening (D) travels into

the chamber (C) in back of the poppet, which causes the

poppet to move due to the difference in the size of the

area on which pressure is exerted between the passage

(B) and the chamber (C). When the poppet moves, the oil

flows from the passage (B) through the hole passage (F)

in the plug and into the tank passage (Ta). This works to

prevent excessive amounts of pressure from being pro-

duced in the negative control signal pressure port.

CONTROL VALVE

3J0AS00

Takeuchi Hydraulic excavator TB1140 (Serial No. 514400002~). Operator's Manual - page 2