WO2002053922A1 - Swing system hydraulic circuit of working machine - Google Patents

Swing system hydraulic circuit of working machine Download PDF

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Publication number
WO2002053922A1
WO2002053922A1 PCT/JP2001/007511 JP0107511W WO02053922A1 WO 2002053922 A1 WO2002053922 A1 WO 2002053922A1 JP 0107511 W JP0107511 W JP 0107511W WO 02053922 A1 WO02053922 A1 WO 02053922A1
Authority
WO
WIPO (PCT)
Prior art keywords
turning
hydraulic
oil
motor
pump
Prior art date
Application number
PCT/JP2001/007511
Other languages
French (fr)
Japanese (ja)
Inventor
Hitoshi Iwasaki
Atsushi Wada
Original Assignee
Shin Caterpillar Mitsubishi Ltd.
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 Shin Caterpillar Mitsubishi Ltd. filed Critical Shin Caterpillar Mitsubishi Ltd.
Publication of WO2002053922A1 publication Critical patent/WO2002053922A1/en

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/167—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load using pilot pressure to sense the demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/36—Pilot pressure sensing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the present invention belongs to the technical field of a swing hydraulic circuit in a working machine having a swing body such as a hydraulic shovel. Background technology ''
  • working machines equipped with a revolving unit such as a hydraulic excavator include, in addition to a revolving motor for revolving the revolving unit, a traveling motor, a hydraulic attachment for a work attachment, and the like.
  • a plurality of hydraulic actuators are provided, and a hydraulic pump serving as a hydraulic supply source for the hydraulic actuators is mounted.
  • one or more main pumps are provided, and the pressure oil supplied from the main pump is configured to be distributed to the rotating motor and the other hydraulic actuators, or to another hydraulic pump.
  • a pump provided with a dedicated pump for a swing motor separately from a main pump for supplying pressure oil to a plurality of hydraulic actuators is conventionally known.
  • the supply pressure oil from the main pump is configured to be distributed to the turning motor and a plurality of other hydraulic actuators.
  • the load on the other hydraulic actuator is light, and the supply pressure oil from the main pump flows preferentially to the other hydraulic actuator and the turning motor is operated.
  • Insufficient supply of pressurized oil for one night resulting in a problem that the turning speed is reduced when the turning and other operations are linked, resulting in poor workability.
  • the pump for turning is operated at the same time as the turning motor and the other hydraulic actuator, the hydraulic oil from the dedicated motor is supplied to the turning motor even when the turning motor is operated at the same time.
  • the present invention has been made in view of the above-mentioned circumstances, and has been created with the object of solving these problems, and a turning motor for turning a revolving body, and a turning motor other than the turning motor.
  • a large-capacity main pump serving as a common hydraulic supply source for the above-mentioned turning module and other hydraulic actuators, and a turning motor dedicated to the turning operation
  • the pump is provided with a small-capacity dedicated pump that serves as a pressure oil supply source, and pressurized oil from both pumps is supplied to the turning motor during turning operation.
  • control valve that controls the supply and discharge of pressure oil in the turning motor is provided with an oil passage through which part of the pressure oil supplied from the main pump during the turning operation flows to the oil tank.
  • the working machine is a shovel-type construction machine equipped with blades
  • the dedicated pump is a pressure oil supply source dedicated to the hydraulic actuator for the blade during blade work, and a pressure oil supply source dedicated to the turning motor during the turning operation.
  • FIG. 1 is a side view of a hydraulic excavator.
  • FIG. 2 is a hydraulic circuit diagram of the excavator.
  • FIG. 3 is a view showing the relationship between the spool movement stroke of the first control valve for turning and the opening area of the center bypass valve path.
  • FIGS. 4 (A) and 4 (B) are diagrams showing the relationship between the flow rate of hydraulic oil supplied to the turning motor and the lever stroke of the turning lever.
  • reference numeral 1 denotes a hydraulic excavator.
  • the hydraulic excavator 1 includes a lower traveling body 2 of a crawler type, an upper revolving body 3 rotatably supported by the lower traveling body 2, and an upper revolving body.
  • the work unit 4 includes various parts such as a work unit 4 mounted on the body 3.
  • the work unit 4 is further supported by the upper revolving unit 3 so as to be able to swing up and down.
  • the lower traveling body comprises a paper boom 6, an arm 7, which is supported by the upper boom 6 so as to be able to swing back and forth, and a bucket 8 attached to a tip end of the arm 7.
  • the basic configuration such as that the blade 9 is supported on the frame 2 so as to be able to swing up and down is the same as before.
  • FIG. 2 the outline of the hydraulic circuit of the hydraulic excavator 1 is shown in FIG. 2, wherein in FIG. 10, 10 and 11 are first and second main pumps, 12 is a dedicated pump, 13 is a pilot pump, 14 is an oil tank, 15 and 16 are left and right running motors, 17 is a turning motor, 18 is a boom cylinder, 19 is an offset cylinder, 20 is an arm cylinder, 21 Is a bucket cylinder and 22 is a blade cylinder.
  • Reference numerals 23 to 33 denote control valves for controlling the supply of pressure oil to the cylinders 15 to 22 described above. Of these control valves 23 to 33, left and right traveling control valves are provided.
  • the second IJ control valve 31 and the bucket control valve 32 are incorporated in the first valve unit 38 as a core valve group, and the swivel second control valve 26 and the blade control valve 3 3 Is incorporated in the second valve unit 34.
  • control valves 23 to 33 the first and second control valves for turning 25, 2
  • the control valves other than 6 are illustrated in a simplified manner, and detailed description thereof is omitted.
  • the first and second main pumps 10 and 11 are variable displacement piston pumps, and are controlled via control pulp 23 to 25 and 27 to 32 of the first valve unit 38.
  • Left and right traveling Left and right traveling motors 15 and 16; turning motor 17 and 17; boom cylinder 18 and offset cylinder 19; arm cylinder 20 and packet cylinder 21 Although it is configured to supply oil, the capacity of these first and second main pumps 10 and 11 is large enough to correspond to the required flow rate of the hydraulic pumps 15 to 21 above. Is set to
  • the dedicated pump 12 is a gear pump, and supplies pressure oil to the turning motor 17 and the blade cylinder 22 via the control valves 26 and 33 of the second valve unit 34.
  • the dedicated pump 12 is capable of responding to the required flow rate of the blade cylinder 17, but has a smaller capacity than the maximum required flow rate of the turning motor 17. ing. The supply of pressurized oil from the dedicated pump 12 to the turning motor 17 will be described later.
  • A shows that the pressure oil of the first main pump 10 is supplied to the control valves 23, 25, 30, 28.
  • B is a first oil bypass passage for flowing oil to the oil tank 14 via B, and B is hydraulic oil for the second main pump 11, and control valves 24, 29, 27, 32, This is the second center bypass oil passage for flowing into the oil tank 14 via 31.
  • C is a parallel oil passage for supplying the pressure oil of the first main pump 10 to the control valves 25, 30 and 28, and D is the pressure oil of the second main pump 11 A parallel oil passage for supplying the control valves 29, 27, 32, 31.
  • E is a tank oil passage for flowing the oil discharged from the control valves 23, 25, 30, 24, 29, 27, 32 to the oil tank 14.
  • the third oil bypass oil passage that flows the pressure oil of the dedicated pump 12 to the oil tank 14 via the control valves 33 and 26?
  • the third parallel oil passage 0 that supplies the pressure oil of the dedicated pump 1 2 to the control valve 26 and the sunset oil passage H that allows the oil discharged from the control valve 33 to flow into the oil passage 14 are formed. I have.
  • the first valve unit 38 and the second valve A junction oil passage I is formed between the unit 34 and the second turning control valve 26 from the first turning control valve 23.
  • the first control pulp 25 for turning is incorporated in the first valve unit 38 as described above, and this is a pilot port 25a for left turning and right turning. , 25b, and in the state where pilot pressure is not input to both pilot ports 25a, 25b, the oil in the first center bus path oil passage A flows downstream.
  • the center bypass valve line PT is opened, and the supply valve line PM for supplying the hydraulic oil of the second parallel oil passage C and the merged oil passage I to the turning motor 17, and the turning motor 1 It is located at the neutral position N, which closes the drainage oil passage MT for flowing the oil discharged from 7 to the tank oil passage E, but it is located at the pilot port 25 a for left turn or the pilot port 25 b for right turn.
  • the pilot pressure PT With narrow, and is configured to Setsu ⁇ Ru so the pressurized oil supply position X or Y to open the discharge Benro MT and the supply valve passage PM.
  • the relationship between the movement stroke of the spool of the first control valve 25 for turning and the opening area of the center bypass valve path PT is shown in FIG. 3, and as shown in FIG.
  • the center bypass valve path PT narrows as the spool travel stroke increases, but does not close even if the spool moves to the full stroke.
  • the part is configured to flow downstream. In other words, even if the first control valve for turning 25 is located at the pressure oil supply position X or Y, part of the pressure oil supplied from the first main pump 10 is transferred to the valve passage PT for the centrifugal bypass.
  • the oil is supplied to the oil tank 14 via the first main pump 10 so as to prevent the supply amount of the pressurized oil from the first main pump 10 from becoming excessive.
  • the second control valve 26 for turning is a two-position switching valve having a pilot port 26a, and this is a state in which the pilot port pressure is not input to the pilot port 26a.
  • the Senda bypass valve line PT for flowing the oil in the third Senda bus path oil passage F to the downstream side is opened, and the pressure oil in the third parallel oil passage G is supplied to the combined oil passage I.
  • the pilot pressure is input to the pilot port 26a, thereby closing the above-mentioned sensor bypass valve line PT and PJ open junction position X It is configured.
  • reference numeral 35 denotes a turning pilot valve
  • the pilot valve 35 operates the turning lever 36 to the left turning side or the right turning side.
  • the pilot pressure is output to the left turning-side pilot port 25a or the right turning-side pilot port 25b of the first turning control valve 25 based on this.
  • the pilot pressure output from the pilot valve 35 becomes the second control valve for turning via the shuttle valve 37.
  • 26 is input to pilot port 26a. That is, when the pilot pressure outputs the pilot pressure from the pilot valve 35 based on the operation of the turning operation lever 36, the pilot pressure moves the turning first control valve 25 to the hydraulic oil supply position X or Y.
  • the second turning control valve 26 switches to the merging position X.
  • the pressure oil of the first main pump 10 supplied via the first parallel oil passage C, the third parallel oil passage, and the second control valve 2 Combined with the pressure oil of the dedicated pump 1 and 2 supplied via the merging valve line PJ and the merging oil line I, via the supply valve line PM of the first swivel control valve 25 It is supplied as such.
  • FIG. 4 (A) shows a schematic diagram of the relationship between the flow rate of the pressurized oil supplied to the turning motor 17 and the lever stroke of the turning operation lever 36.
  • the relationship between the pressure oil supply flow rate and the lever stroke can be set, for example, to the relationship shown in FIG. 4 (B).
  • the dedicated pump 12 serves as a pressure oil supply source for the blade cylinder 22 in addition to the turning motor 17, but since the turning operation and the blade operation are not usually performed at the same time, The pressure oil of the pump 12 is supplied exclusively to the turning motor 17 during the turning operation, and is supplied exclusively to the blade cylinder 22 during the blade operation.
  • the turning motor 17 has a dedicated pump 12 that supplies pressure oil to the turning motor 17 only during turning operation, and a turning motor 17 Pressure oil is supplied from both pumps including the first main pump 10 which is a pressure oil supply source for a plurality of hydraulic actuators.
  • the pressurized oil from the first main pump 10 is also supplied, so that the turning operation can be performed quickly.
  • the turning operation is performed in conjunction with other operations such as boom raising and arm out
  • the supply pressure oil from the first main pump 10 flows preferentially to other hydraulic actuators for turning. Even if the supply to the motor 17 is insufficient, the pressure oil from the dedicated pump 12 is exclusively supplied to the motor 17 for turning, so the speed of the motor 17 for turning decreases when linked. Can be avoided.
  • a favorable turning speed can be obtained both independently and in conjunction with each other, thereby improving workability.
  • the first control valve for turning 25 is connected to the first main pump 1 even if it is located at the pressure oil supply position X or Y for supplying the pressurized oil to the turning moder 17. Since a part of the supply pressure oil from 0 is flowed to the oil tank 14 via the valve path PT for the Sendai Bypass, excessive pressure oil is supplied from the first main pump 10. It is possible to eliminate a bite of energy.
  • the dedicated pump 12 is a pressure oil supply source for the blade cylinder 22 in addition to the turning motor 17, and the blade operation is performed in conjunction with other operations.
  • the blade operation and the turning operation are not usually performed in conjunction with each other.
  • it is configured so that the speed can be changed without changing the speed.
  • a dedicated hydraulic pump is provided, and in such a case, the dedicated hydraulic pump for the blade can be used as it is to implement the dedicated pump of the present invention, which is convenient.
  • the turning motor includes a large-capacity main pump serving as a pressure oil supply source for a plurality of hydraulic actuators and a small-capacity dedicated pump serving as a pressure oil supply source dedicated to the turning motor during the turning operation.
  • Pressure oil from both pumps will be supplied.

Abstract

A swing system hydraulic circuit of a working machine capable of providing a desirable swing speed in both a swing operation alone and a swing operation interlocked with the operations of the other hydraulic actuators, comprising a large capacity main pump (10) as a common hydraulic oil supply source for a swing motor (17) and the other hydraulic actuators and a small capacity exclusive pump (12) as a hydraulic oil supply source used exclusively for the swing motor in swing operation, wherein, in the swing operation, pressurized oil is supplied from both pumps to the swing motor.

Description

明 細 書 作業機械における旋回系油圧回路 技術分野  Description Hydraulic circuit for swivel system in work machines
本発明は、 油圧ショベル等の旋回体を備えた作業機械における旋回系油圧回路 の技術分野に属するものである。 背景技術 '  The present invention belongs to the technical field of a swing hydraulic circuit in a working machine having a swing body such as a hydraulic shovel. Background technology ''
一般に、 油圧ショベル等の旋回体を備えた作業機械には、 旋回体を旋回せしめ るための旋回用モ一夕に加えて、 走行用モ一夕、 作業アタッチメント用油圧ァク チユエ一夕等の複数の油圧ァクチユエ一夕が設けられていると共に、 これら複数 の油圧ァクチユエ一夕の油圧供給源となる油圧ポンプが搭載されている。 この場 合、 一つまたは複数のメインポンプを設け、 該メインポンプからの供給圧油を旋 回用モ一夕および他の複数の油圧ァクチユエ一夕に配分するように構成したもの 、 あるいは他の複数の油圧ァクチユエ一夕に圧油を供給するメインポンプとは別 に、 旋回モー夕用に専用のポンプを設けたもの等が、 従来知られている。  In general, working machines equipped with a revolving unit such as a hydraulic excavator include, in addition to a revolving motor for revolving the revolving unit, a traveling motor, a hydraulic attachment for a work attachment, and the like. A plurality of hydraulic actuators are provided, and a hydraulic pump serving as a hydraulic supply source for the hydraulic actuators is mounted. In this case, one or more main pumps are provided, and the pressure oil supplied from the main pump is configured to be distributed to the rotating motor and the other hydraulic actuators, or to another hydraulic pump. Conventionally, a pump provided with a dedicated pump for a swing motor separately from a main pump for supplying pressure oil to a plurality of hydraulic actuators is conventionally known.
ところで、 前記従来のものにおいて、 メインポンプからの供給圧油を旋回用モ 一夕および他の複数の油圧ァクチユエ一夕に配分するように構成したものは、 旋 回用モ一夕と他の油圧ァクチユエ一夕とを同時に作動させる場合、 他の油圧ァク チユエ一夕の負荷が軽 、と該他の油圧ァクチユエ一夕側にメインポンプからの供 給圧油が優先的に流れて旋回用モ一夕への圧油供給量が不足し、 この結果、 旋回 と他の作動との連動時に旋回スピードが低下して作業性に劣るという問題がある これに対し、 旋回用モ一夕用に専用のポンプを設けたものは、 旋回用モ一夕と 他の油圧ァクチユエ一夕とを同時に作動させる場合でも旋回用モー夕には専用モ 一夕からの圧油が供給されるため、 連動時における旋回スピードの低下という問 題はないが、 上言己専用ポンプはエンジン馬力をメインポンプと分配することにな るため、 他の複数の油圧ァクチユエ一夕の作業性を考慮すると専用ポンプを小容 量のものにせざるを得ず、 この結果、 前記メインポンプからの圧油を旋回用モ一 夕に供給するように構成したものに比べて、 旋回作動を単独で行う場合の旋回ス ピードが遅くなって作業性に劣るという問題があり、 ここに本発明が解決しょう とする課題があった。 発明の開示 ' By the way, in the above-mentioned conventional apparatus, the supply pressure oil from the main pump is configured to be distributed to the turning motor and a plurality of other hydraulic actuators. When the actuator is operated at the same time, the load on the other hydraulic actuator is light, and the supply pressure oil from the main pump flows preferentially to the other hydraulic actuator and the turning motor is operated. Insufficient supply of pressurized oil for one night, resulting in a problem that the turning speed is reduced when the turning and other operations are linked, resulting in poor workability. Even if the pump for turning is operated at the same time as the turning motor and the other hydraulic actuator, the hydraulic oil from the dedicated motor is supplied to the turning motor even when the turning motor is operated at the same time. Although there is no problem of lowering the turning speed, Since the pump dedicated to the engine distributes the engine horsepower to the main pump, the capacity of the dedicated pump is small considering the workability of other hydraulic actuators. As a result, the turning speed when the turning operation is performed alone is slower than that in the case where the hydraulic oil from the main pump is supplied to the turning motor alone as a result. Therefore, there is a problem that the workability is poor, and there is a problem to be solved by the present invention. DISCLOSURE OF THE INVENTION ''
本発明は、 上記の如き実情に鑑み、 これらの課題を解決することを目的として 創作されたものであって、 旋回体を旋回せしめるための旋回用モー夕と、 該旋回 用モ一夕以外の他の油圧ァクチユエ一夕を備えてなる作業機械において、 上記旋 回用モ一夕および他の油圧ァクチユエ一夕の共通の油圧供給源となる大容量のメ ィンポンプと、 旋回作動時に旋回用モータ専用の圧油供給源となる小容量の専用 ポンプとを設け、 旋回作動時にはこれら両ポンプからの圧油が旋回用モータに供 給される構成にしたものである。  SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and has been created with the object of solving these problems, and a turning motor for turning a revolving body, and a turning motor other than the turning motor. For a work machine equipped with another hydraulic actuator, a large-capacity main pump serving as a common hydraulic supply source for the above-mentioned turning module and other hydraulic actuators, and a turning motor dedicated to the turning operation The pump is provided with a small-capacity dedicated pump that serves as a pressure oil supply source, and pressurized oil from both pumps is supplied to the turning motor during turning operation.
そして、 この様にすることにより、 旋回作動の単独時、 他の油圧ァクチユエ一 夕との連動時の何れにおいても好適な旋回スピードが得られることになつて、 作 業性が向上する。  By doing so, a suitable turning speed can be obtained both when the turning operation is performed alone and when the hydraulic operation is performed in conjunction with another hydraulic actuator, and the workability is improved.
このものにおいて、 旋回用モ一夕の圧油供給排出制御を行う制御バルブに、 旋 回作動時にメインポンプから供給される圧油の一部を油タンクに流すための油路 を形成することにより、 メインポンプからの圧油供給量が過剰にならないように コントロールできる。  In this system, the control valve that controls the supply and discharge of pressure oil in the turning motor is provided with an oil passage through which part of the pressure oil supplied from the main pump during the turning operation flows to the oil tank. However, it is possible to control the supply of pressurized oil from the main pump not to be excessive.
また、 作業機械はブレードを備えたショベル系建設機械であって、 専用ポンプ は、 ブレード作業時にはブレード用油圧ァクチユエ一夕専用の圧油供給源となり 、 旋回作動時には旋回用モータ専用の圧油供給源となるように設定することによ り、 一つの専用ポンプを有効利用して、 ブレード作業と旋回作動との両方の作業 性の向上を計ることができる。 図面の簡単な説明  The working machine is a shovel-type construction machine equipped with blades, and the dedicated pump is a pressure oil supply source dedicated to the hydraulic actuator for the blade during blade work, and a pressure oil supply source dedicated to the turning motor during the turning operation. By setting so as to be able to effectively use one dedicated pump, it is possible to improve the workability of both the blade work and the turning operation. BRIEF DESCRIPTION OF THE FIGURES
第 1図は油圧ショベルの側面図である。  FIG. 1 is a side view of a hydraulic excavator.
第 2図は 油圧ショベルの油圧回路図である。 第 3図は旋回用第一制御バルブのスプール移動ストロ一クとセンタバイパス 用弁路開口面積との関係を示す図である。 FIG. 2 is a hydraulic circuit diagram of the excavator. FIG. 3 is a view showing the relationship between the spool movement stroke of the first control valve for turning and the opening area of the center bypass valve path.
第 4図 （A) 、 (B ) は旋回用モー夕への圧油供給流量と旋回用レバーのレ バーストロークとの関係を示す図である。  FIGS. 4 (A) and 4 (B) are diagrams showing the relationship between the flow rate of hydraulic oil supplied to the turning motor and the lever stroke of the turning lever.
発明を実施するための最良の形態 BEST MODE FOR CARRYING OUT THE INVENTION
次に、 本発明の実施の形態を図面に基づいて説明する。 第 1図において、 1は 油圧ショベルであって、 該油圧ショベル 1は、 クロ一ラ式の下部走行体 2、 該下 部走行体 2に旋回自在に支持される上部旋回体 3、 該上部旋回体 3に装着される 作業部 4等の各部を備えており、 さらに該作業部 4は、 上部旋回体 3に上下揺動 自在に支持されるロアブーム 5、 該ロアブーム 5に左右揺動自在に支持されるァ ヅパ一ブーム 6、 該アッパーブーム 6に前後揺動自在に支持されるアーム 7、 該 アーム 7の先端部に取付けられるバケツト 8等の部材装置から構成され、 また、 前記下部走行体 2のフレームには、 プレード 9が上下揺動自在に支持されている 等の基本的構成は、 従来通りである。  Next, embodiments of the present invention will be described with reference to the drawings. In FIG. 1, reference numeral 1 denotes a hydraulic excavator. The hydraulic excavator 1 includes a lower traveling body 2 of a crawler type, an upper revolving body 3 rotatably supported by the lower traveling body 2, and an upper revolving body. The work unit 4 includes various parts such as a work unit 4 mounted on the body 3. The work unit 4 is further supported by the upper revolving unit 3 so as to be able to swing up and down. The lower traveling body comprises a paper boom 6, an arm 7, which is supported by the upper boom 6 so as to be able to swing back and forth, and a bucket 8 attached to a tip end of the arm 7. The basic configuration such as that the blade 9 is supported on the frame 2 so as to be able to swing up and down is the same as before.
扨、 前記油圧ショベル 1の油圧回路の概略を第 2図に示すが、 第 2図において 、 1 0、 1 1は第一、 第二メインポンプ、 1 2は専用ポンプ、 1 3はパイロヅト ポンプ、 1 4は油タンク、 1 5、 1 6は左右の走行モー夕、 1 7は旋回用モー夕 、 1 8はブーム用シリンダ、 1 9はオフセヅト用シリンダ、 2 0はアーム用シリ ンダ、 2 1はバケツト用シリンダ、 2 2はブレード用シリンダである。 また、 2 3〜 3 3は上記モ一夕、 シリンダ 1 5〜 2 2に対する圧油供給制御を行う制御バ ルブであって、 これら制御バルブ 2 3〜3 3のうち、 左右の走行用制御バルブ 2 3、 2 4、 旋回用第一制御バルブ 2 5、 ブーム用第一制御バルブ 2 7、 ブーム用 第二制御バルブ 2 8、 オフセット用制御バルブ 2 9、 アーム用第一制御バルブ 3 0、 アーム用第二 IJ御バルブ 3 1、 バケヅト用制御バルブ 3 2は、 コアバルブグ ループとして第一バルブユニット 3 8内に組み込まれており、 また、 旋回用第二 制御バルブ 2 6およびブレード用制御バルブ 3 3は、 第二バルブュニット 3 4内 に組み込まれている。  Now, the outline of the hydraulic circuit of the hydraulic excavator 1 is shown in FIG. 2, wherein in FIG. 10, 10 and 11 are first and second main pumps, 12 is a dedicated pump, 13 is a pilot pump, 14 is an oil tank, 15 and 16 are left and right running motors, 17 is a turning motor, 18 is a boom cylinder, 19 is an offset cylinder, 20 is an arm cylinder, 21 Is a bucket cylinder and 22 is a blade cylinder. Reference numerals 23 to 33 denote control valves for controlling the supply of pressure oil to the cylinders 15 to 22 described above. Of these control valves 23 to 33, left and right traveling control valves are provided. 2 3, 2 4, 1st control valve for swing 25, 1st control valve for boom 2 7, 2nd control valve for boom 2 8, Offset control valve 29, 1st control valve for arm 30, Arm The second IJ control valve 31 and the bucket control valve 32 are incorporated in the first valve unit 38 as a core valve group, and the swivel second control valve 26 and the blade control valve 3 3 Is incorporated in the second valve unit 34.
尚、 前記制御バルブ 2 3〜3 3のうち、 旋回用第一、 第二制御バルブ 2 5、 2 6以外の制御バルブについては簡略化して図示すると共に、 その詳細な説明は省 略する。 Among the control valves 23 to 33, the first and second control valves for turning 25, 2 The control valves other than 6 are illustrated in a simplified manner, and detailed description thereof is omitted.
前記第一、 第二メインポンプ 1 0、 1 1は、 可変容量型のピストン式ポンプで あって、 前記第一バルブュニヅト 3 8の制御パルプ 2 3〜2 5、 2 7〜 3 2を介 して左右の走行左右の走行モ一夕 1 5、 1 6、 旋回用モ一夕 1 7、 ブーム用シリ ンダ 1 8、 オフセット用シリンダ 1 9、 アーム用シリンダ 2 0、 パケット用シリ ンダ 2 1に圧油を供給するように構成されているが、 これら第一、 第二メインポ ンプ 1 0、 1 1の容量は、 上記複数の油圧ァクチユエ一夕 1 5〜2 1の要求流量 に対応するべく大容量に設定されている。  The first and second main pumps 10 and 11 are variable displacement piston pumps, and are controlled via control pulp 23 to 25 and 27 to 32 of the first valve unit 38. Left and right traveling Left and right traveling motors 15 and 16; turning motor 17 and 17; boom cylinder 18 and offset cylinder 19; arm cylinder 20 and packet cylinder 21 Although it is configured to supply oil, the capacity of these first and second main pumps 10 and 11 is large enough to correspond to the required flow rate of the hydraulic pumps 15 to 21 above. Is set to
また、 専用ポンプ 1 2はギヤ式ポンプであって、 第二バルブュニヅト 3 4の制 御バルブ 2 6、 3 3を介して旋回用モータ 1 7、 ブレ一ド用シリンダ 2 2に圧油 を供給するように構成されているが、 該専用ポンプ 1 2は、 プレード用シリンダ 1 7の要求流量には対応できるが、 旋回用モ一夕 1 7の最大要求流量に対しては 少なめの容量に設定されている。 尚、 専用ポンプ 1 2から旋回用モータ 1 7への 圧油供給については後述する。  The dedicated pump 12 is a gear pump, and supplies pressure oil to the turning motor 17 and the blade cylinder 22 via the control valves 26 and 33 of the second valve unit 34. The dedicated pump 12 is capable of responding to the required flow rate of the blade cylinder 17, but has a smaller capacity than the maximum required flow rate of the turning motor 17. ing. The supply of pressurized oil from the dedicated pump 12 to the turning motor 17 will be described later.
ここで、 前記第一バルブュニット 3 8に形成される油路について簡単に説明す ると、 Aは、 第一メインポンプ 1 0の圧油を、 制御バルブ 2 3、 2 5、 3 0、 2 8を経由して油タンク 1 4に流すための第一セン夕バイパス油路であり、 Bは、 第二メインポンプ 1 1の圧油を、 制御バルブ 2 4、 2 9、 2 7、 3 2、 3 1を経 由して油タンク 1 4に流すための第二センタバイパス油路である。 また Cは、 第 一メインポンプ 1 0の圧油を、 制御バルブ 2 5、 3 0、 2 8に供給するためのパ ラレル油路であり、 Dは、 第二メインポンプ 1 1の圧油を、 制御バルブ 2 9、 2 7、 3 2、 3 1に供給するためのパラレル油路である。 さらに Eは、 制御バルブ 2 3、 2 5、 3 0、 2 4、 2 9、 2 7、 3 2からの排出油を油タンク 1 4に流す ためのタンク油路である。 また同様に、 第二バルブユニット 3 4においても、 専 用ポンプ 1 2の圧油を制御バルブ 3 3、 2 6を経由して油タンク 1 4に流す第三 セン夕バイパス油路？、 専用ポンプ 1 2の圧油を制御バルブ 2 6に供給する第三 パラレル油路0、 および制御バルブ 3 3からの排出油を油夕ンク 1 4に流す夕ン ク油路 Hが形成されている。 さらに、 前記第一バルブユニット 3 8と第二バルブ ュニヅト 3 4とのあいだには、 旋回用第二制御バルブ 2 6から旋回用第一制御バ ルブ 2 3に至る合流油路 Iが形成されている。 Here, the oil passage formed in the first valve unit 38 will be briefly described. A shows that the pressure oil of the first main pump 10 is supplied to the control valves 23, 25, 30, 28. B is a first oil bypass passage for flowing oil to the oil tank 14 via B, and B is hydraulic oil for the second main pump 11, and control valves 24, 29, 27, 32, This is the second center bypass oil passage for flowing into the oil tank 14 via 31. C is a parallel oil passage for supplying the pressure oil of the first main pump 10 to the control valves 25, 30 and 28, and D is the pressure oil of the second main pump 11 A parallel oil passage for supplying the control valves 29, 27, 32, 31. E is a tank oil passage for flowing the oil discharged from the control valves 23, 25, 30, 24, 29, 27, 32 to the oil tank 14. Similarly, in the second valve unit 34 as well, the third oil bypass oil passage that flows the pressure oil of the dedicated pump 12 to the oil tank 14 via the control valves 33 and 26? The third parallel oil passage 0 that supplies the pressure oil of the dedicated pump 1 2 to the control valve 26 and the sunset oil passage H that allows the oil discharged from the control valve 33 to flow into the oil passage 14 are formed. I have. Further, the first valve unit 38 and the second valve A junction oil passage I is formed between the unit 34 and the second turning control valve 26 from the first turning control valve 23.
一方、 前記旋回用第一制御パルプ 2 5は、 前述したように第一バルブユニット 3 8に組み込まれているが、 このものは、 左旋回用、 右旋回用のパイロットポ一 ト 2 5 a、 2 5 bを備えた三位置切換弁であって、 両パイロヅトポート 2 5 a、 2 5 bにパイロット圧が入力されていない状態では、 第一センタバスパス油路 A の油を下流側に流すためのセンタバイパス用弁路 P Tを開き、 且つ、 第二パラレ ル油路 Cおよび前記合流油路 Iの圧油を旋回用モータ 1 7に供給するための供給 用弁路 P Mと、 旋回用モータ 1 7からの排出油をタンク油路 Eに流すための排出 用油路 M Tとを閉じる中立位置 Nに位置しているが、 左旋回用パイロヅトポート 2 5 aまたは右旋回用パイロットポート 2 5 bにパイロット圧が入力されること により、 上記セン夕バイパス用弁路 P Tを絞ると共に、 供給用弁路 P Mと排出用 弁路 M Tとを開く圧油供給位置 Xまたは Yに切換るように構成されている。 ここで、 前記旋回用第一制御バルブ 2 5のスプールの移動ストロークと、 セン タバイパス用弁路 P Tの開口面積との関係を第 3図に示すが、 該第 3図に示され るように、 センタバイパス用弁路 P Tは、 スプールの移動ストロークが大きくな るにつれて絞られていくが、 スプールがフルストロークまで移動しても閉鎖する ことなく、 第一セン夕バイパス油路 Aの圧油の一部を下流側に流すように構成さ れている。 つまり、 旋回用第一制御バルブ 2 5は、 圧油供給位置 Xまたは Yに位 置していても、 第一メインポンプ 1 0からの供給圧油の一部をセン夕バイパス用 弁路 P Tを介して油タンク 1 4に流すようになつており、 これにより第一メイン ポンプ 1 0からの圧油供給量が過剰にならないようにコントロールされている。 また、 前記旋回用第二制御バルブ 2 6は、 パイロヅトポート 2 6 aを備えた二 位置切換弁であって、 このものは、 パイロットポート 2 6 aにパイ口ヅト圧が入 力されていない状態では、 第三セン夕バスパス油路 Fの油を下流側に流すための セン夕バイパス用弁路 P Tを開き、 且つ、 第三パラレル油路 Gの圧油を合流油路 Iに供給するための合流用弁路 P Jを閉じる中立位置 Nに位置しているが、 パイ ロットポート 2 6 aにパイロット圧が入力されることにより、 上記セン夕バイパ ス用弁路 P Tを閉じると共に、 合流用弁路 P Jを開く合流位置 X 切換るように 構成されている。 On the other hand, the first control pulp 25 for turning is incorporated in the first valve unit 38 as described above, and this is a pilot port 25a for left turning and right turning. , 25b, and in the state where pilot pressure is not input to both pilot ports 25a, 25b, the oil in the first center bus path oil passage A flows downstream. The center bypass valve line PT is opened, and the supply valve line PM for supplying the hydraulic oil of the second parallel oil passage C and the merged oil passage I to the turning motor 17, and the turning motor 1 It is located at the neutral position N, which closes the drainage oil passage MT for flowing the oil discharged from 7 to the tank oil passage E, but it is located at the pilot port 25 a for left turn or the pilot port 25 b for right turn. The pilot pressure PT With narrow, and is configured to Setsu換Ru so the pressurized oil supply position X or Y to open the discharge Benro MT and the supply valve passage PM. Here, the relationship between the movement stroke of the spool of the first control valve 25 for turning and the opening area of the center bypass valve path PT is shown in FIG. 3, and as shown in FIG. The center bypass valve path PT narrows as the spool travel stroke increases, but does not close even if the spool moves to the full stroke. The part is configured to flow downstream. In other words, even if the first control valve for turning 25 is located at the pressure oil supply position X or Y, part of the pressure oil supplied from the first main pump 10 is transferred to the valve passage PT for the centrifugal bypass. The oil is supplied to the oil tank 14 via the first main pump 10 so as to prevent the supply amount of the pressurized oil from the first main pump 10 from becoming excessive. Further, the second control valve 26 for turning is a two-position switching valve having a pilot port 26a, and this is a state in which the pilot port pressure is not input to the pilot port 26a. Then, the Senda bypass valve line PT for flowing the oil in the third Senda bus path oil passage F to the downstream side is opened, and the pressure oil in the third parallel oil passage G is supplied to the combined oil passage I. Although it is located at the neutral position N, which closes the merged valve line PJ, the pilot pressure is input to the pilot port 26a, thereby closing the above-mentioned sensor bypass valve line PT and PJ open junction position X It is configured.
さらに、 前記第 2図の油圧回路において、 3 5は旋回用のパイ口ットバルブで あって、 該パイロットバルブ 3 5は、 旋回用レバー 3 6を左旋回側または右旋回 側に操作することに基づき、 前記旋回用第一制御バルブ 2 5の左旋回側パイロッ トポート 2 5 aまたは右旋回側パイロットポート 2 5 bにパイロヅト圧を出力す る。 さらに、 旋回用レバー 3 6を左旋回側、 右旋回側の何れに操作した場合でも 、 前記パイロットバルブ 3 5から出力されたパイロット圧は、 シャトル弁 3 7を 介して旋回用第二制御バルブ 2 6のパイロヅトポート 2 6 aに入力される。 つまり、 旋回用操作レバ一 3 6の操作に基づいてパイロヅトバルブ 3 5からノ イロヅ ト圧が出力されると、 該パイロット圧により、 旋回用第一制御バルブ 2 5 が圧油供給位置 Xまたは Yに切換ると共に、 旋回用第二制御バルブ 2 6が合流位 置 Xに切換る。 これにより、 旋回用モ一夕 1 7には、 第一パラレル油路 Cを経由 して供給される第一メインポンプ 1 0の圧油と、 第三パラレル油路 、 旋回用第 二制御バルブ 2 6の合流用弁路 P J、 合流油路 Iを経由して供給される専用ボン プ 1 2の圧油とが合流したものが、 旋回用第一制御バルブ 2 5の供給用弁路 P M を経由して供給されるようになっている。  Further, in the hydraulic circuit shown in FIG. 2, reference numeral 35 denotes a turning pilot valve, and the pilot valve 35 operates the turning lever 36 to the left turning side or the right turning side. The pilot pressure is output to the left turning-side pilot port 25a or the right turning-side pilot port 25b of the first turning control valve 25 based on this. Further, even when the turning lever 36 is operated to the left turning side or the right turning side, the pilot pressure output from the pilot valve 35 becomes the second control valve for turning via the shuttle valve 37. 26 is input to pilot port 26a. That is, when the pilot pressure outputs the pilot pressure from the pilot valve 35 based on the operation of the turning operation lever 36, the pilot pressure moves the turning first control valve 25 to the hydraulic oil supply position X or Y. At the same time, the second turning control valve 26 switches to the merging position X. As a result, the pressure oil of the first main pump 10 supplied via the first parallel oil passage C, the third parallel oil passage, and the second control valve 2 Combined with the pressure oil of the dedicated pump 1 and 2 supplied via the merging valve line PJ and the merging oil line I, via the supply valve line PM of the first swivel control valve 25 It is supplied as such.
ここで、 前記旋回用モータ 1 7に対する圧油供給流量と、 旋回用操作レバー 3 6のレバ一ストロークとの関係の概略図を第 4図 （A) に示すが、 該第 4図 （A ) に示されるように、 専用ポンプ 1 2からの圧油供給量だけでは不足する分を、 第一メインポンプ 1 0からの圧油供給で補うようになっている。 この場合、 圧油 供給流量とレバーストロークとの関係は、 例えば第 4図 （B ) に示すような関係 に設定することもできる。  Here, FIG. 4 (A) shows a schematic diagram of the relationship between the flow rate of the pressurized oil supplied to the turning motor 17 and the lever stroke of the turning operation lever 36. As shown in FIG. As shown in (1), the shortage of pressure oil supply from the dedicated pump 12 alone is compensated for by the supply of pressure oil from the first main pump 10. In this case, the relationship between the pressure oil supply flow rate and the lever stroke can be set, for example, to the relationship shown in FIG. 4 (B).
尚、 専用ポンプ 1 2は、 旋回用モ一夕 1 7の他にブレード用シリンダ 2 2の圧 油供給源となっているが、 旋回作動とブレード操作とを同時に行うことは通常な いため、 専用ポンプ 1 2の圧油は、 旋回操作時には専ら旋回用モー夕 1 7に供給 され、 またブレード操作時には専らブレード用シリンダ 2 2に供給されるように なっている。  The dedicated pump 12 serves as a pressure oil supply source for the blade cylinder 22 in addition to the turning motor 17, but since the turning operation and the blade operation are not usually performed at the same time, The pressure oil of the pump 12 is supplied exclusively to the turning motor 17 during the turning operation, and is supplied exclusively to the blade cylinder 22 during the blade operation.
叙述の如く構成されたものにおいて、 旋回用モータ 1 7には、 旋回作動時には 専ら旋回用モ一夕 1 7に圧油を供給する専用ポンプ 1 2と、 旋回用モ一夕 1 7も 含めて複数の油圧ァクチユエ一夕の圧油供給源である第一メインポンプ 1 0との 両方のポンプからの圧油が供給されることになる。 In the motor configured as described above, the turning motor 17 has a dedicated pump 12 that supplies pressure oil to the turning motor 17 only during turning operation, and a turning motor 17 Pressure oil is supplied from both pumps including the first main pump 10 which is a pressure oil supply source for a plurality of hydraulic actuators.
この結果、 エンジン馬力の配分の関係上、 専用ポンプ 1 2の容量が旋回用モ一 夕 1 7の最大要求量に対して小さめのものであっても、 旋回作動を単独で行う場 合には、 専用ポンプ 1 2からの供給圧油に加えて第一メインポンプ 1 0からの圧 油も供給されることになつて、 旋回作動をスピーディに行うことができる。 一方 、 旋回作動を、 ブーム上昇やアームアウト等の他の作動と連動で行う場合には、 第一メインポンプ 1 0からの供給圧油が他の油圧ァクチユエ一夕に優先的に流れ て旋回用モー夕 1 7への供給量が不足しても、 旋回用モ一夕 1 7には専用ポンプ 1 2からの圧油が専ら供給されるから、 連動時に旋回用モータ 1 7のスピードが 低下してしまうことを回避できる。 而して、 単独時、 連動時の何れにおいても好 適な旋回スピードが得られることになつて、 作業性が向上する。  As a result, due to the distribution of engine horsepower, even if the capacity of the dedicated pump 12 is smaller than the maximum demand of the In addition to the supply of the pressurized oil from the dedicated pump 12, the pressurized oil from the first main pump 10 is also supplied, so that the turning operation can be performed quickly. On the other hand, when the turning operation is performed in conjunction with other operations such as boom raising and arm out, the supply pressure oil from the first main pump 10 flows preferentially to other hydraulic actuators for turning. Even if the supply to the motor 17 is insufficient, the pressure oil from the dedicated pump 12 is exclusively supplied to the motor 17 for turning, so the speed of the motor 17 for turning decreases when linked. Can be avoided. Thus, a favorable turning speed can be obtained both independently and in conjunction with each other, thereby improving workability.
しかもこのものにおいて、 旋回用第一制御バルブ 2 5は、 旋回用モーダ 1 7に 圧油を供給する圧油供給位置 Xまたは Yに位置している状態であっても、 第一メ インポンプ 1 0からの供給圧油の一部を、 セン夕パイパス用弁路 P Tを介して油 タンク 1 4に流すように構成されているから、 第一メインポンプ 1 0から過剰の 圧油が供給されてしまうエネルギ一口スを無くすことができる。  Further, in this case, the first control valve for turning 25 is connected to the first main pump 1 even if it is located at the pressure oil supply position X or Y for supplying the pressurized oil to the turning moder 17. Since a part of the supply pressure oil from 0 is flowed to the oil tank 14 via the valve path PT for the Sendai Bypass, excessive pressure oil is supplied from the first main pump 10. It is possible to eliminate a bite of energy.
また、 本実施の形態では、 専用ポンプ 1 2は、 旋回用モータ 1 7の他にブレー ド用シリンダ 2 2の圧油供給源となっていて、 ブレード作動を、 他の作動と連動 で行う場合であっても （前述したように、 ブレード作動と旋回作動とは連動で行 うことは通常ない） 速度変化することなく行うことができるように構成されてい るが、 既存の油圧ショベルのなかにはブレード専用の油圧ポンプが設けられたも のがあり、 このようなものにおいては、 該ブレード専用の油圧ポンプをそのまま 利用して本発明の専用ポンプとして実施することができ、 好都合である。 産業上の利用可能性  Further, in this embodiment, the dedicated pump 12 is a pressure oil supply source for the blade cylinder 22 in addition to the turning motor 17, and the blade operation is performed in conjunction with other operations. However, as described above, the blade operation and the turning operation are not usually performed in conjunction with each other. However, it is configured so that the speed can be changed without changing the speed. There is a case where a dedicated hydraulic pump is provided, and in such a case, the dedicated hydraulic pump for the blade can be used as it is to implement the dedicated pump of the present invention, which is convenient. Industrial applicability
本発明において、 旋回用モ一夕には、 複数の油圧ァクチユエ一夕の圧油供給源 となる大容量のメインポンプと、 旋回作動時に旋回モータ専用の圧油供給源とな る小容量の専用ポンプとの両方のポンプからの圧油が供給されることになる。 こ の結果、 旋回作動を単独で行う場合には、 両方のポンプからの圧油供給により旋 回作動をスピーディに行うことができる一方、 旋回作動を他の油圧ァクチュエー 夕の作動と連動で行う場合には、 メインポンプの圧油が他の油圧ァクチユエ一夕 に優先的に流れても、 旋回モータには専用ポンプの圧油が専ら供給されることに なって、 旋回スピードの低下を回避でき、 而して単独時、 連動時の何れにおいて も好適な旋回スピ一ドが得られることになつて、 作業性が向上する。 In the present invention, the turning motor includes a large-capacity main pump serving as a pressure oil supply source for a plurality of hydraulic actuators and a small-capacity dedicated pump serving as a pressure oil supply source dedicated to the turning motor during the turning operation. Pressure oil from both pumps will be supplied. This As a result, when the swing operation is performed independently, the swing operation can be speedily performed by supplying the hydraulic oil from both pumps, while the swing operation is performed in conjunction with the operation of other hydraulic actuators. In other words, even if the pressure oil of the main pump flows preferentially to other hydraulic equipment, the pressure oil of the dedicated pump is exclusively supplied to the swing motor, so that a decrease in the swing speed can be avoided. In addition, a suitable turning speed can be obtained both independently and in conjunction with each other, thereby improving workability.

Claims

請 求 の 範 囲 The scope of the claims
1 . 旋回体を旋回せしめるための旋回用モー夕と、 該旋回用モ一夕以外の他 の油圧ァクチユエ一夕を備えてなる作業機械において、 上記旋回用モータおよび 他の油圧ァクチユエ一夕の共通の油圧供給源となる大容量のメインポンプと、 旋 回作動時に旋回用モータ専用の圧油供給源となる小容量の専用ポンプとを設け、 旋回作動時にはこれら両ポンプからの圧油が旋回用モータに供給される構成にし たことを特徴とする作業機械における旋回系油圧回路。 1. In a working machine including a turning motor for turning the revolving body and a hydraulic actuator other than the turning motor, the turning motor and the other hydraulic actuator are common. A large-capacity main pump is provided as a hydraulic pressure supply source, and a small-capacity dedicated pump is provided as a small-capacity oil supply source dedicated to the slewing motor during slewing operation. A turning hydraulic circuit for a working machine, characterized in that it is supplied to a motor.
2 . 請求項 1において、 旋回用モー夕の圧油供給排出制御を行う制御バルブ は、 旋回作動時にメインポンプから供給される圧油の一部を油タンクに流すため の油路が形成されていることを特徴とする作業機械における旋回系油圧回路。  2. In claim 1, the control valve for controlling the supply and discharge of the pressurized oil of the turning motor is provided with an oil passage for flowing a part of the pressure oil supplied from the main pump to the oil tank during the turning operation. A hydraulic hydraulic circuit for a swing machine in a working machine.
3 . 請求項 1または 2において、 作業機械はブレードを備えたショベル系建 設機械であって、 専用ポンプは、 ブレード作業時にはブレード用油圧ァクチユエ —夕専用の圧油供給源となり、 旋回作動時には旋回用モ一夕専用の圧油供給源と なるように設定されていることを特徴とする作業機械における旋回系油圧回路。  3. The work machine according to claim 1 or 2, wherein the work machine is a shovel-based construction machine equipped with a blade, and the dedicated pump serves as a hydraulic oil supply source for the blade during the blade work, and a turning source during the turning operation. A swivel hydraulic circuit for a working machine, wherein the hydraulic circuit is set to be a pressure oil supply source dedicated to a working machine.
PCT/JP2001/007511 2000-12-28 2001-08-30 Swing system hydraulic circuit of working machine WO2002053922A1 (en)

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Application Number Priority Date Filing Date Title
JP2000401976A JP2002195206A (en) 2000-12-28 2000-12-28 Hydraulic circuit for slewing system in working machine
JP2000-401976 2000-12-28

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CN102166832A (en) * 2011-01-17 2011-08-31 合肥合锻机床股份有限公司 Energy-saving and consumption-reducing hydraulic system with multistage pressure control for large hydraulic machine
JP6290644B2 (en) * 2014-02-07 2018-03-07 ナブテスコ株式会社 Hydraulic drive

Citations (6)

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JPS53132106A (en) * 1977-04-22 1978-11-17 Komatsu Mfg Co Ltd Hydraulic circuit for top turning excavator
JPS54109230U (en) * 1978-01-11 1979-08-01
JPS6386170U (en) * 1986-11-19 1988-06-06
JPH0617447A (en) * 1991-02-27 1994-01-25 Yutani Heavy Ind Ltd Hydraulic circuit of small shovel
WO1998012391A1 (en) * 1996-09-19 1998-03-26 Yanmar Diesel Engine Co., Ltd. Hydraulic circuit for turning excavator
JPH11210022A (en) * 1998-01-29 1999-08-03 Yanmar Diesel Engine Co Ltd Slewing service car

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53132106A (en) * 1977-04-22 1978-11-17 Komatsu Mfg Co Ltd Hydraulic circuit for top turning excavator
JPS54109230U (en) * 1978-01-11 1979-08-01
JPS6386170U (en) * 1986-11-19 1988-06-06
JPH0617447A (en) * 1991-02-27 1994-01-25 Yutani Heavy Ind Ltd Hydraulic circuit of small shovel
WO1998012391A1 (en) * 1996-09-19 1998-03-26 Yanmar Diesel Engine Co., Ltd. Hydraulic circuit for turning excavator
JPH11210022A (en) * 1998-01-29 1999-08-03 Yanmar Diesel Engine Co Ltd Slewing service car

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