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WO2018032496A1 - Compacteur de surface - Google Patents

Compacteur de surface Download PDF

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Publication number
WO2018032496A1
WO2018032496A1 PCT/CN2016/095980 CN2016095980W WO2018032496A1 WO 2018032496 A1 WO2018032496 A1 WO 2018032496A1 CN 2016095980 W CN2016095980 W CN 2016095980W WO 2018032496 A1 WO2018032496 A1 WO 2018032496A1
Authority
WO
WIPO (PCT)
Prior art keywords
compactor
drum
hydraulic pump
fluid line
axle brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2016/095980
Other languages
English (en)
Inventor
Alan Liu
Yeager WANG
Jeff DIAO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volvo Construction Equipment AB
Original Assignee
Volvo Construction Equipment AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volvo Construction Equipment AB filed Critical Volvo Construction Equipment AB
Priority to PCT/CN2016/095980 priority Critical patent/WO2018032496A1/fr
Publication of WO2018032496A1 publication Critical patent/WO2018032496A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K7/0015—Disposition of motor in, or adjacent to, traction wheel the motor being hydraulic
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/26—Rollers therefor; Such rollers usable also for compacting soil self-propelled or fitted to road vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/40—Special vehicles
    • B60Y2200/41—Construction vehicles, e.g. graders, excavators
    • B60Y2200/413—Compactors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation

Definitions

  • the present disclosure relates to a surface compactor, more particularly, to a surface compactor that is to be moved for towing by simply releasing an axle brake and a drum brake even if an engine is abnormally in a stop state.
  • a surface compactor In general, a surface compactor is well known as a mobile vehicle that propels itself with hydraulic pressure generated by an engine to level the ground.
  • the surface compactor includes at least one drum disposed at the front of the vehicle body to roll on the ground, and a pair of wheels disposed at the rear of the car body.
  • the surface compactor is equipped with a brake system for decelerating and stopping the drum and the wheels. During compaction work, the vehicle body is propelled to compact the soil, while the drum presses the surface of the soil on the ground, thereby increasing the density of the soil.
  • the compactor disclosed in this Patent Document is a compaction machine used suitably for pavement of a road surface, such as a tire roller, which includes braking units for a drum brake and an axle brake.
  • the brake units are designed to maintain a braking state, when the engine is shut down. If an engine stops due to breakdown or malfunction of an engine during compaction work, the compactor remains in braking state at the work site. An operator has to take a step to enable the vehicle to tow in order to repair the surface compactor.
  • axle brake and the drum brake should be able to be forcibly unlocked for towing and the compactor should be allowed to move.
  • a surface compactor comprising a first variable displacement hydraulic pump, a fixed displacement hydraulic pump and a propelling motor hydraulically connected to the first variable displacement hydraulic pump in a closed loop hydraulic circuit, the first variable displacement hydraulic pump and the fixed displacement hydraulic pump being connected to an engine; a drum motor hydraulically connected to a second variable displacement hydraulic pump and configured to drive the drum; an axle brake including an axle brake cylinder, the axle brake cylinder being connected to the fixed displacement hydraulic pump via an axle brake fluid line and configured to release a braking state of an axle; a drum brake including a drum brake cylinder and a gear module connected to the second variable hydraulic pump, the drum brake cylinder being connected to the fixed displacement hydraulic pump via a drum brake fluid line branched off from the axle brake fluid line and configured to release a braking state of the drum; and a towing control valve disposed in the axle brake fluid line, and including a reciprocating pump configured to provide a pressurized fluid from a hydraulic tank to both the axle brake cylinder and
  • the towing control valve further comprises a first flow path connected to the axle brake fluid line via an inlet port and an outlet port; an orifice formed in the first flow path between the inlet port and the outlet port; a second flow path branched off from the first flow path, and configured to communicate the first flow path with a hydraulic tank; and a plurality of check valves disposed in the second flow path.
  • the towing control valve is detachably connected to the axle brake fluid line by a joint connection.
  • FIG. 1 is a side view of the configuration of an entire surface compactor according to an embodiment of the present disclosure.
  • FIG. 2 is a hydraulic circuit diagram related to a propelling system of the surface compactor shown in FIG. 1.
  • FIG. 3 is a hydraulic circuit diagram related to a drum and a drum brake of the surface compactor shown in FIG. 1.
  • FIG. 4 is a perspective view showing a towing control valve of the present disclosure.
  • FIG. 5 is a hydraulic circuit diagram of the towing control valve shown in FIG. 4.
  • FIG. 1 illustrates the schematic configuration of an entire surface compactor.
  • a compactor 1 is composed of a front drum 2, a pair of rear wheels 3, a front body 4, and a rear body 5.
  • a driver's seat 6 is mounted either on the front body 4 or on the rear body 5.
  • a brake manipulation member 9, such as an axle brake button or an axle parking brake button, may be installed adjacent to the driver’s seat 6.
  • the compactor 1 is a soil compactor.
  • the bodies 4, 5 are connected with each other by means of a pivot joint 7 so that the compactor 1 can be steered.
  • the rear wheels 3 can be replaced by a rear drum in certain applications.
  • FIG. 2 is a hydraulic circuit diagram related to a propelling system of the compactor shown in FIG. 1.
  • a closed loop hydraulic circuit is provided for driving the compactor 1. More particularly, the closed loop hydraulic circuit has a variable displacement &reversible first variable displacement hydraulic pump 11 driven by a diesel engine 10, and a propelling motor 12, such as a fixed displacement hydraulic motor, connected to a drive train (not shown) .
  • the first variable displacement hydraulic pump 11 and the propelling motor 12 are fluidly connected by a first conduit 13 and a second conduit 14.
  • the first variable displacement hydraulic pump 11 may be an axial reciprocating pump of which the fluid displacement can be determined by a tilted angle of swash plate 11a.
  • a pump regulator 8 is provided for changing the angle of the swash plate 11a, which may be adjusted with a control valve (not shown) .
  • the flow rate discharged from of the pump 11 can be varied continuously. Namely, if the swash plate 11a is perpendicular to the axis of rotation, i.e., a zero angle, no fluid will flow and the speed of the propelling motor 10 is zero. If it is at a sharp angle, a large volume of fluid will be pumped and the speed of the propelling motor 12 is increased.
  • the first variable displacement hydraulic pump 11 allows the swash plate 11a to be moved in both directions from the zero position, pumping fluid in either direction without reversing the rotation of the first variable displacement hydraulic pump 11.
  • the swash plate angle can vary from a zero angle, i.e., a neutral position, to a positive angle and to a negative angle. Consequently, propelling motors 12a, 12b are caused to rotate in a forward direction and a reverse direction, which correspond to the intended forward or backward travel movement of the vehicle.
  • the first conduit (or the second conduit 14) of the circuit 10 can be a high-pressure supply line or a low-pressure return line.
  • the first conduit 13 becomes a supply line and the second conduit 14 becomes a return line when the propelling motor 12 rotates in the forward direction, i.e., when the compactor 1 travels forward.
  • a fixed displacement hydraulic pump 15, also driven via the engine 10, is installed a flow path 17 which is connected between the first conduit 13 and the second conduit 14, and is configured to compensate for any possible loss of hydraulic pressure associated with the hydraulic circuit when the engine 10 is in a normal operation without malfunction or breakdown and the propel motor 12 is actuated by the first variable hydraulic pump 11.
  • a fluid from the fixed displacement hydraulic pump 15 can be provided for brake release. More detailed explanation will be described later.
  • first and second main relief valves 18, 19 are provided between the first conduit 13 and the second conduit 14 and protect each conduit from pressure overload during operation.
  • the overload pressure generated from either of the first conduit 13 or the second conduit 14 may be introduced through a branch line 20 during compaction or propulsion of the vehicle.
  • the first main relief valve 18 provides a relief function for the first conduit 13
  • the second main relief valve 19 provides a relief function for the second conduit 14.
  • an axle brake 23 includes an axle brake cylinder 25 and the axle brake cylinder 25 is connected to the fixed displacement hydraulic pump 15 via an axle brake fluid line 26 and configured to release a braking state of an axle.
  • the axle brake cylinder 25 includes a pair of cylinders 51a, 51b, and the axle brake 23 is configured to release an axle by manipulation of the brake manipulation member 9, such an axle parking brake button.
  • a brake control valve 24 is disposed between an axle brake cylinder 25 and a branch line 21 which is fluidly in communication with the fixed displacement hydraulic pump 15, and a fluid for releasing the axle brake 23 is selectively applied to the axle brake cylinder 25 through an axle brake fluid line 26 in response to an operation of the brake manipulation member 9.
  • the brake control valve 24 may include an electric control valve, which can be controlled by a solenoid signal or an electromagnetic pilot signal in response to an operation of the brake manipulation member 9.
  • the brake control valve 24 can be switched to an open position by an operation of the brake manipulation member 9. Then, the fluid from the fixed displacement hydraulic pump 15 is supplied to the chamber of the axle brake cylinder 25 through the axle brake fluid line 26, so that the axle brake 23 is in brake release state and the rear wheel 3 is capable of moving or propelling on the ground.
  • the compactor 1 comprises a towing control valve 40.
  • the towing control valve 40 is disposed in the axle brake fluid line 26, and includes a reciprocating pump 41.
  • the towing control valve 40 includes at least one pressure sensor 45 that is disposed close to the first outlet port 49 and the pressure sensor 45 detects and indicates a pressure generated in the axle brake fluid line 26 by operating the reciprocating pump 41.
  • the pressure sensor 45 is installed at the axle brake fluid line 26.
  • the pressure sensor 45 may be installed at the drum brake fluid line 35.
  • the pressure sensor 45 may be a pressure gauge.
  • an additional sensor can be installed at the upstream point of the drum brake fluid line 35 branched off from the axle brake fluid line 26.
  • the pressure sensor 45 may be a pressure gauge.
  • FIG. 3 is a hydraulic circuit diagram related to a drum and a drum brake of the surface compactor shown in FIG. 1.
  • a second variable displacement hydraulic pump 31 having a swash plate 31a is driven by the engine 10 and is connected with a drum brake 50 via a shaft 38.
  • the second variable displacement hydraulic pump 31 is configured such that the tilted angle of the swash plate 31a is controlled by a pump regulator 32.
  • a control valve 36 is connected to a chamber of a pump regulator 33 by flow paths 33a, 33b and controls a hydraulic fluid in response to a valve control signal applied from the outside, so that the pump regulator 33 adjusts volumetrically the tilt angle of the swash plate 31a of the second variable displacement hydraulic pump 31.
  • the second variable displacement hydraulic pump 31 allows the swash plate 30a to be moved in both directions from the zero position.
  • the swash plate angle of the second variable displacement hydraulic pump 31 can vary from a zero angle, i.e., a neutral position, to a positive angle and to a negative angle via the pump regulator 32. Consequently, the second variable displacement hydraulic pump 31 is caused to rotate the drum 2 in a forward direction and a reverse direction, which correspond to the intended forward or backward travel movement of the compactor 1.
  • the rotational speed of the drum 2 may be increased or decreased, depending on the tilted angle of the swash plate 30a.
  • a drum brake 50 includes a drum brake cylinder 34 and a gear module 37 which is connected to the second variable hydraulic pump 31 and the drum brake cylinder 34 is connected to the fixed displacement hydraulic pump 15 via a drum brake fluid line 35 branched off from the axle brake fluid line 26 and be configured to release a braking state of the drum 2.
  • the drum brake cylinder 34 having a chamber is installed a gear module 37 and is configured to communicate with the axle brake fluid line 26 through the drum brake fluid line 35.
  • the drum brake fluid line 35 is connected to the axle brake fluid line 26 at an upstream point of the axle brake cylinder 25.
  • the brake control valve 24 can be switched to an open position by an operation of the brake manipulation member 9. Then, the fluid from the fixed displacement hydraulic pump 15 is supplied to the chamber of the drum brake cylinder 34 through the axle brake fluid line 26 and the drum brake fluid line 35, so that the drum brake 50 is in brake release state and the drum 2 is capable of moving on the ground.
  • the axle brake 23 or the drum brake 50 may include a conventional wet disk brake.
  • FIG. 4 is a perspective view showing a control valve according to the present disclosure and FIG. 5 is a hydraulic circuit diagram of the control valve shown in FIG. 4.
  • the compactor 1 comprises a towing control valve 40 disposed in the axle brake fluid line 26, and is configured to adjust a pressurized fluid delivered from a hydraulic tank T to both the axle brake cylinder 25 and the drum brake cylinder 34 in case where the engine is abnormally in a stop state.
  • the towing control valve 40 includes a reciprocating pump 41 configured to provide a pressurized fluid from a hydraulic tank T to both the axle brake cylinder 25 and drum brake cylinder 34 in case where the engine 10 stops, so that the compactor is movably operated for towing.
  • the towing control valve 40 includes a first flow path 46 which is connected to the axle brake fluid line 26 via an inlet port 48a and an outlet port 49. Also, the towing control valve 40 includes an orifice 44 formed in the first flow path 46 between the inlet port 48a and the outlet port 49, a second flow path 47 branched off from the first flow path 46. The second flow path 47 is configured to communicate the first flow path 46 with a hydraulic tank T via a second inlet port 48b.
  • the hydraulic tank T may be composed of an auxiliary hydraulic tank.
  • the towing control valve 40 comprises a plurality of check valves 49 that are disposed in the second flow path 47.
  • the reciprocating pump 41 is installed at the second flow path 47 between the check valves 49, and may control a flow mount or a flow rate of the pressurized fluid from a hydraulic tank T to both the axle brake cylinder 25 and drum brake cylinder 34.
  • the fluid sucked from the hydraulic tank T by the reciprocating pump 41 is pressurized or pumped out, and be delivered to the axle brake cylinder 25 and the drum brake cylinder 34 via the outlet port 49, the axle brake fluid line 26 and the drum brake fluid line 35 with a predetermined brake release pressure.
  • the predetermined brake release pressure may be adaptive for various ranges in response to the requirements for achieving brake release.
  • the reciprocating pump 41 includes a lever 42 and a plunger 43 which is connected to the lever 42, and the plunger 43 is reciprocated in the cylinder of the reciprocating pump 41 by external force applied to the lever 42.
  • the check valves 49 include a first check valve 49a for preventing backflow of the brake release fluid flow from the first fluid path 46.
  • the first check valve 49a is configured to prevent backflow of the pressurized fluid from the axle brake fluid line 26 in case where the engine 10 stops.
  • the check valves 49 include a second check valve 49b for preventing backflow of the pressurized fluid from the cylinder of the reciprocating pump 41
  • the towing control valve 40 includes a rotational switch 51 thread-fastened to a valve housing 52 to adjust an opening degree of the orifice 44.
  • the rotational switch 51 alternatively includes a needle valve for adjusting an open state or a closed state of the first flow path 46 in case where the engine 10 stops.
  • the towing control valve 40 may be detachably connected to the axle brake fluid line by a joint connection.
  • the joint connection may be configured by brake line connecting hoses which are connected to the inlet port 48a and the outlet port 49, respectively.
  • the first flow path 46 or the orifice 44 of the towing control valve 40 is maintained by an open position at the axle brake fluid line 26.
  • the first flow path 46 or the orifice 44 of the towing control valve 40 can be changed in a closed position at the axle brake fluid line 26.
  • the axle brake cylinder 25 and the drum brake cylinder 34 are fluidly in communication to the hydraulic tank T via the reciprocating pump 41 of the towing control valve 40.
  • the reciprocating pump 41 provides a pressurized fluid delivered from a hydraulic tank T to both the axle brake cylinder 25 and the drum brake cylinder 34.
  • the reciprocating pump 41 may be operated manually by the operator.
  • the pressurized fluid in the cylinder of the reciprocating pump 41 is provided through the first check valve 49a of the towing control valve 40 and the axle brake fluid line 26, and it can be delivered until a pressure in the chamber of the axle brake cylinder 25 reaches 20 to 24 bar.
  • the axle brake 25 is released by the pressurized fluid, and thus the wheel 3 can be moved.
  • the pressurized fluid in the cylinder of the reciprocating pump 41 flows into a drum brake releasing channel 35 via the axle brake fluid line 26 and the drum brake fluid line 35.
  • the drum brake 50 is released by the pressurized fluid, and thus the drum 2 can be moved.
  • the pressurized fluid required for brake release and generated in the axle brake fluid line 26 and the drum brake fluid line 35 may be variously set as a predetermined brake release pressure, depending on the specifications of the compactor or brake units applicable for the compactor. For example, a pressure larger than 24bars may be provided by a predetermined brake release pressure.
  • the surface compactor having a towing control valve according to the present disclosure is advantageous in that, even if a brake is maintained in a braking state due to stopping of an engine when the engine breaks down or a malfunction occurs in the engine, an operator can easily release the axle brake and the drum brake, thus capable of towing the compactor for maintenance.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Road Paving Machines (AREA)

Abstract

La présente invention concerne un compacteur de surface (1) comprenant au moins un tambour (2) destiné à presser une surface en roulant sur le sol, ledit compacteur de surface comprenant : une première pompe hydraulique à déplacement variable (11), une pompe hydraulique à déplacement fixe (15) et un moteur de propulsion (12) relié hydrauliquement à la première pompe hydraulique à déplacement variable dans un circuit hydraulique en boucle fermée, la première pompe hydraulique à déplacement variable et la pompe hydraulique à déplacement fixe étant reliées à un moteur (10); un moteur-tambour (30) relié hydrauliquement à une seconde pompe hydraulique à déplacement variable (31) et configuré pour entraîner le tambour ; et une soupape de commande de remorquage (40) disposée dans la conduite de fluide de frein d'essieu (26) et comprenant une pompe volumétrique alternative (41) configurée de sorte à fournir un fluide sous pression à partir d'un réservoir hydraulique (T) à la fois au cylindre de frein d'essieu (25) et au cylindre de frein à tambour (34) dans le cas où le moteur s'arrête, de telle sorte que le compacteur soit actionné de façon mobile en vue d'un remorquage.
PCT/CN2016/095980 2016-08-19 2016-08-19 Compacteur de surface Ceased WO2018032496A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2016/095980 WO2018032496A1 (fr) 2016-08-19 2016-08-19 Compacteur de surface

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2016/095980 WO2018032496A1 (fr) 2016-08-19 2016-08-19 Compacteur de surface

Publications (1)

Publication Number Publication Date
WO2018032496A1 true WO2018032496A1 (fr) 2018-02-22

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PCT/CN2016/095980 Ceased WO2018032496A1 (fr) 2016-08-19 2016-08-19 Compacteur de surface

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WO (1) WO2018032496A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190136877A1 (en) * 2017-11-08 2019-05-09 Applied Industrial Technologies, Inc. Hydraulic Braking Emergency Utilization for Steering, Braking, Charging Accumulators(s), and/or Work Functions to Reduce or Prevent Engine from Overspeed, Assist Acceleration and/or Unlimited Towing

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5336019A (en) * 1993-05-10 1994-08-09 Hollon Edmund D Uniform compaction of asphalt concrete
CN2425127Y (zh) * 2000-05-01 2001-03-28 厦工集团三明重型机器有限公司 压路机手动供油拖引液压机构
CN200961232Y (zh) * 2006-10-20 2007-10-17 西安筑路机械有限公司 养护专用压路机
CN102066148A (zh) * 2008-06-19 2011-05-18 卡特彼勒路面机械公司 静液传动式压实机中多个推进泵的方法和布置
CN103821068A (zh) * 2012-11-16 2014-05-28 陕西中大机械集团有限责任公司 双钢轮压路机防打滑系统
CN205478612U (zh) * 2016-04-05 2016-08-17 山推工程机械股份有限公司 一种工程机械液压制动系统

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5336019A (en) * 1993-05-10 1994-08-09 Hollon Edmund D Uniform compaction of asphalt concrete
CN2425127Y (zh) * 2000-05-01 2001-03-28 厦工集团三明重型机器有限公司 压路机手动供油拖引液压机构
CN200961232Y (zh) * 2006-10-20 2007-10-17 西安筑路机械有限公司 养护专用压路机
CN102066148A (zh) * 2008-06-19 2011-05-18 卡特彼勒路面机械公司 静液传动式压实机中多个推进泵的方法和布置
CN103821068A (zh) * 2012-11-16 2014-05-28 陕西中大机械集团有限责任公司 双钢轮压路机防打滑系统
CN205478612U (zh) * 2016-04-05 2016-08-17 山推工程机械股份有限公司 一种工程机械液压制动系统

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190136877A1 (en) * 2017-11-08 2019-05-09 Applied Industrial Technologies, Inc. Hydraulic Braking Emergency Utilization for Steering, Braking, Charging Accumulators(s), and/or Work Functions to Reduce or Prevent Engine from Overspeed, Assist Acceleration and/or Unlimited Towing
US11156237B2 (en) * 2017-11-08 2021-10-26 Applied Industrial Technologies, Inc. Hydraulic braking emergency utilization for steering, braking, charging accumulator(s), and/or work functions to reduce or prevent engine from overspeed, assist acceleration and/or unlimited towing
US11674532B2 (en) 2017-11-08 2023-06-13 Applied Industrial Technologies, Inc. Hydraulic braking energy utilization for emergency steering, braking, charging accumulator(s), and/or work functions to reduce or prevent engine from overspeed, assist acceleration and/or unlimited towing

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