JPH02212606A - Hydraulic flow control device for construction machine - Google Patents
Hydraulic flow control device for construction machineInfo
- Publication number
- JPH02212606A JPH02212606A JP1032884A JP3288489A JPH02212606A JP H02212606 A JPH02212606 A JP H02212606A JP 1032884 A JP1032884 A JP 1032884A JP 3288489 A JP3288489 A JP 3288489A JP H02212606 A JPH02212606 A JP H02212606A
- Authority
- JP
- Japan
- Prior art keywords
- control
- valve
- valves
- control signal
- flow rate
- 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.)
- Granted
Links
- 238000010276 construction Methods 0.000 title claims description 18
- 239000002131 composite material Substances 0.000 claims description 32
- 238000006073 displacement reaction Methods 0.000 claims description 19
- 150000001875 compounds Chemical class 0.000 claims description 14
- 230000001105 regulatory effect Effects 0.000 claims description 6
- 230000001276 controlling effect Effects 0.000 claims 1
- 230000035945 sensitivity Effects 0.000 abstract 2
- 239000003921 oil Substances 0.000 description 21
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Landscapes
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、一対の複合制御弁と一対の可変容量ポンプと
からなる建設機械の油圧流量制御装置に係り、更に詳細
には前記建設機械における両複合制御弁の間に設けられ
る圧油合流用連通弁の開閉制御装置並びに可変容量ポン
プの吐出量制御装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic flow control device for construction machinery comprising a pair of compound control valves and a pair of variable displacement pumps, and more specifically relates to a hydraulic flow control device for construction machinery. The present invention relates to an opening/closing control device for a pressure oil merging communication valve provided between both composite control valves and a discharge amount control device for a variable displacement pump.
従来のこの種の建設機械における油圧装置は、一般に第
４図に示すように、それぞれ２つのアクチュエータ１２
ａ、１２ｂ並びに３２ａ、３２ｂを操作する方向切換弁
１４ａ。The conventional hydraulic system in this type of construction machine generally has two actuators 12 each, as shown in FIG.
a, 12b and 32a, 32b.
１４ｂ並びに３４ａ、３４ｂを有する一対の複合制御弁
１０．３０と、これら複合制御弁１０．３０の各々に圧
油を供給する一対の可変容量ポンプ１６．３６とからな
る。なお、前記アクチュエータ１２ ａ 、 １２
ｂ 、 ３２ ａ、 。It consists of a pair of compound control valves 10.30 having valves 14b, 34a, and 34b, and a pair of variable displacement pumps 16.36 that supply pressure oil to each of these compound control valves 10.30. Note that the actuators 12a, 12
b, 32a, .
３２ｂは通常それぞれ旋回用、アーム用、ブーム用、パ
ケット用に供せられる。前記方向切換弁１４ａ、１４ｂ
、３４ａ、３４ｂはそれぞれ圧力補償弁１８ａ、１８ｂ
、３８ａ。32b is usually provided for swinging, arm, boom, and packet, respectively. The directional control valves 14a, 14b
, 34a and 34b are pressure compensating valves 18a and 18b, respectively.
, 38a.
３８ｂｆ！−備え、そしてそれぞれ制御信号発生装置２
０ ａ 、 ２０ ｂ 、 ４０ ａ 、 ４０１）に
よって制御される。また、両複合制御弁１０゜３０の間
は連通弁４２によって相互に連通され、そして前記連通
弁４２は制御信号発生装置２０ｂ、４０ａによって開閉
操作される。38bf! - a control signal generator 2;
0 a , 20 b , 40 a , 401 ). Further, the two composite control valves 10 and 30 are communicated with each other by a communication valve 42, and the communication valve 42 is opened and closed by the control signal generators 20b and 40a.
従って、このような構成になる油圧装置は、各アクチュ
エータ１２ａ、１２ｂ、３２ａ３２ｂがそれぞれ制御信
号発生装置２０ａ。Therefore, in the hydraulic system having such a configuration, each actuator 12a, 12b, 32a32b is a control signal generating device 20a.
２０ｂ、４０ａ、４０ｂによって制御操作されると共に
、更にこの場合、圧油が大流量を要求されるアクチュエ
ータ１２ｂ、３２ａの操作時には、制御信号発生装置２
０ｂ。The control signal generator 2
0b.
４０ａの操作によって連通弁４２が連通され、アクチュ
エータ１２ｂ、３２ａには両ポンプ１６．３６の吐出圧
油が合流して供給される。By operating the valve 40a, the communication valve 42 is brought into communication, and the pressure oil discharged from both the pumps 16 and 36 is combined and supplied to the actuators 12b and 32a.
従って、大容量を要求されるアクチュエータ１２ｂ、３
２ａすなわちアーム用並びにブーム用アクチュエータを
必要に応じて高速で運転できる利点を有する。Therefore, actuators 12b and 3 that require large capacity
2a, that is, the arm actuator and boom actuator can be operated at high speed as required.
しかしながら、前述した従来の油圧装置における前記利
点は、アーム用あるいはブーム用アクチュエータの何れ
か一方が単独で運転される際にのみ達成されるものであ
り、両アクチュエータが同時に運転される際には逆に次
のような難点を有していた。すなわち、従来の油圧装置
においては、アーム用並びにブーム用アクチュエータが
同時に運転されると、両ポンプの吐出圧油は、連通弁を
介して合流し両アクチュエータに同時に作用するが、こ
の合流された吐出圧油は、両アクチュエータの中の負荷
圧力の低い方のアクチュエータ側のみに供給される。従
って、負荷圧力の高い方のアクチュエータは作動されな
いという問題が発生した。このことは、建設機械の操作
性並びに安全性を阻害するものであった。However, the above-mentioned advantages in the conventional hydraulic system are achieved only when either the arm or boom actuator is operated independently, and vice versa when both actuators are operated simultaneously. had the following difficulties. In other words, in conventional hydraulic systems, when the arm and boom actuators are operated simultaneously, the discharge pressure oil of both pumps merges through the communication valve and acts on both actuators simultaneously. Pressure oil is supplied only to the actuator side with the lower load pressure among both actuators. Therefore, a problem occurred in that the actuator with the higher load pressure was not operated. This impeded the operability and safety of construction machinery.
そこで、本発明の目的は、両複合制御弁におけるそれぞ
れ大流量側のアクチュエータが同時に操作された際にも
、両アクチュエータを同時に駆動可能とすると共に、更
に両ポングの吐出圧油の合流量を任意所定に設定し得る
ようにした建設機械の油圧流量制御装置を提供すること
にある。Therefore, an object of the present invention is to make it possible to simultaneously drive both actuators even when the actuators on the high flow rate side of both compound control valves are operated simultaneously, and to also arbitrarily control the merging amount of pressure oil discharged from both pumps. An object of the present invention is to provide a hydraulic flow control device for construction machinery that can be set to a predetermined value.
先の目的を達成するため、本発明に係る建設機械の油圧
流量制御装置は、各々に少くともアクチュエータを操作
するための２つの方向切換弁を有する一対の複合制御弁
と、これら複合制御弁の各々にそれぞれ圧油を供給する
一対の可変容量ポンプと、前記方向切換弁の操作量をそ
れぞれ制御する複数の制御信号発生装置と、前記一対の
複合制御弁の間を相互に連通ずる連通弁とからなる油圧
流量制御装置において、
前記複合制御弁をクローズドセンタ型とし、前記可変容
量ポンプを負荷感応制御型とし、前記複合制御弁と前記
負荷感応制御型可変容量ポンプとの間に流量調整弁を設
け、前記制御信号発生装置の制御信号および／もしくは
制御信号量で前記連通弁を開閉すると共に、前記制御信
号発生装置の制御信号量で前記流量調整弁の開度を調整
してこの流量調整弁の前後の圧力を前記負荷感応制御型
可変容量ポンプの制御部に印加するよう構成することを
特徴とする。In order to achieve the above object, a hydraulic flow control device for construction machinery according to the present invention includes a pair of composite control valves each having at least two directional control valves for operating an actuator, and a pair of composite control valves each having at least two directional control valves for operating an actuator. a pair of variable displacement pumps that respectively supply pressure oil; a plurality of control signal generators that respectively control the operation amount of the directional control valves; and a communication valve that communicates between the pair of composite control valves. In the hydraulic flow control device, the composite control valve is a closed center type, the variable displacement pump is a load sensitive control type, and a flow rate adjustment valve is provided between the composite control valve and the load sensitive variable displacement pump. the communication valve is opened and closed by the control signal and/or the amount of the control signal of the control signal generator, and the opening degree of the flow rate regulating valve is adjusted by the amount of the control signal of the control signal generating device; The present invention is characterized in that it is configured to apply pressures before and after the above to the control section of the load-sensitive variable displacement pump.
この場合、連通弁は、両複合制御弁における方向切換弁
の制御信号が互いに対向して印加され、前記制御信号の
双方の信号量が略等しいかもしくは共に作用していない
際には前記両複舒制御弁の間をブロックするかもしくは
絞りを連通し、前記制御信号の双方の信号量が異なるか
もしくは一方のみが作用している際には両複合制御弁の
間を連通ずるよう構成する。In this case, when the control signals of the directional control valves in both the composite control valves are applied opposite to each other, and the signal amounts of both of the control signals are approximately equal or do not act together, the communication valve is configured to control the communication valve. The control valves are blocked or communicated with a throttle, and when the amounts of both control signals are different or when only one of them is acting, the two compound control valves are communicated with each other.
また、予め定められた特定の方向切換弁の制御信号発生
装置の操作により、連通弁は両複合制御弁の間を連通し
、前記特定の方向切換弁を含まない側の複合制御弁に接
続された負荷感応制御型可変容量ポンプはそのポンプ吐
出流量をポンプ最大吐出流量以下の任意の流量に規制さ
れるよう構成する。Further, by operating a control signal generator for a predetermined specific directional switching valve, the communication valve communicates between both the composite control valves and is connected to the composite control valve on the side that does not include the specific directional switching valve. The load-sensitive control type variable displacement pump is configured such that its pump discharge flow rate is regulated to an arbitrary flow rate below the pump maximum discharge flow rate.
両複合制御弁におけるそれぞれ大流量側のアクチュエー
タ、例えはアーム用並びにブーム用アクチュエータを、
同時に高速運転するために両ポンプの吐出圧油を全量合
流すべくそれぞれの制御信号発生装置を共に最大量操作
すると、この場合連通弁に対向して印加される信号量は
等しくなるので連通弁がブロックされる。このため、両
ポンプの吐出圧油は合流されず、両アクチュエータには
それぞれのポンプの吐出流量か供給される。従って、両
アクヂュエータは単独操作時の略半分の速度ではあるが
作動を停止されることなく双方共互いに独立して駆動さ
れる。一方、バケツ１〜用などの小容量アクチュエータ
を増速させるために他方のポンプの吐出圧油を合流させ
る際には、前記アクチュエータの制御信号量の所定の割
合の信号量か前記ポンプの流量調整弁に出力され、これ
により前記ポンプの吐出流量が所定量増量され、この増
量分の圧油か連通弁を介してバケツ１〜アクヂュエータ
に供給される。従って、パケットアクチュエータは制御
操作された高速度で効率良く駆動される。The actuators on the large flow side of both composite control valves, for example, the actuators for the arm and the boom,
In order to simultaneously operate at high speed, the control signal generators of both pumps are operated to the maximum amount in order to merge the entire amount of discharge pressure oil. Blocked. Therefore, the discharge pressure oils of both pumps are not combined, and both actuators are supplied with the discharge flow rate of each pump. Therefore, both actuators are driven independently of each other without stopping their operation, although the speed is approximately half that of when they are operated alone. On the other hand, when the discharge pressure oil of the other pump is merged with the other pump in order to increase the speed of a small capacity actuator such as bucket 1~, the flow rate of the pump is adjusted by a signal amount of a predetermined proportion of the control signal amount of the actuator. This increases the discharge flow rate of the pump by a predetermined amount, and this increased amount of pressure oil is supplied to the bucket 1 to the actuator via the communication valve. Therefore, the packet actuator is efficiently driven at a controlled high speed.
次に、本発明に係る建設機械の油圧流量制御装置の一実
施例につき添付図面を参照しながら以下詳細に説明する
。なお、説明の便宜上、第４図に示す従来の構成と同一
構成部分については、同一参照符号を付しその詳細な説
明を省略する。Next, an embodiment of the hydraulic flow control device for construction machinery according to the present invention will be described in detail below with reference to the accompanying drawings. For convenience of explanation, the same reference numerals are given to the same components as the conventional structure shown in FIG. 4, and detailed explanation thereof will be omitted.
本発明に係る建設機械の油圧流量制御装置は、第１図に
示すように、それぞれ２つのアクチュエータ１２ａ、１
２ｂ並びに３２ａ。As shown in FIG. 1, the hydraulic flow control device for construction machinery according to the present invention has two actuators 12a and 1, respectively.
2b and 32a.
３２ｂを操作する方向切換弁１．４ａ、１４．ｂ並びに
３４ａ、３４ｂを有する一対の複合制御弁５０．５２と
、これら複合制御弁５０５２の各々に圧油を供給する一
対の可変客足ポンプ５４．５６とからなる。なお、前記
アクチュエータ１２ａ １２ｂ ３２ａ３２ｂは通
常それぞれ旋回用、アーム用、ブーム用、バケツ１〜用
に供せられる。前記方向切換弁１４ａ、１４ｂ、３４ａ
、３４ｂは、それぞれ圧力補償弁１８ａ、１８ｂ、３８
ａ３８ｂを備え、そしてそれぞれ制御信号発生装置２０
ａ、２０ｂ ４０ａ ４０ｂによって制御される。Directional switching valves 1.4a, 14.32b operated. It consists of a pair of compound control valves 50.52 having valves 50.b, 34a and 34b, and a pair of variable traffic pumps 54.56 that supply pressure oil to each of these compound control valves 5052. Note that the actuators 12a, 12b, and 32a32b are normally used for swinging, arm, boom, and bucket 1 to 1, respectively. The directional control valves 14a, 14b, 34a
, 34b are pressure compensation valves 18a, 18b, 38, respectively.
a38b, and each control signal generator 20
a, 20b 40a 40b.
また、両複合制御弁５０５２の間は連通弁５８によって
相互に連通される。Further, the two composite control valves 5052 are communicated with each other by a communication valve 58.
しかるに、本発明の油圧流量制御装置においては、複合
制御弁５０．５２はクローズドセンタ型とされ、可変容
量ポンプ５４．５６は負荷感応制御型とされる。そして
、前記負荷感応制御型可変容量ポンプ５４．５６ （以
降単にポンプと称する）とクローズドセンタ型複合制御
弁５０．５２ （以降単に複合制御弁と称する）の各制
御信号発生装置２０ａ。However, in the hydraulic flow control system of the present invention, the compound control valve 50.52 is of the closed center type, and the variable displacement pump 54.56 is of the load sensitive control type. and each control signal generating device 20a of the load sensitive control type variable displacement pump 54, 56 (hereinafter simply referred to as pump) and the closed center type composite control valve 50, 52 (hereinafter simply referred to as composite control valve).
２０ｂ並びに４０ａ、４０ｂとの間には、それぞれ制御
演算装置６０．６２を介して流量調整弁６４．６６が設
けられる。なお、制御演算装置６０は、複合制御弁５０
におけるアクチュエータ１２ａ、１２ｂ用の制御信号発
生装置２０ａ、２０ｂの出力制御信号量と複合制御弁５
２における合流を要するアクチュエータ３２ａ、３２ｂ
用の制御信号発生装置４０ａ、’４０ｂの出力制御信号
量との合計となる合計出力制御信号量が、ポンプ５４の
最大吐出流量を越えた時に、この最大吐出量に対応する
出力制御信号量を、流量調整弁６４に出力する。制御演
算装置６２は、アクチュエータ３２ａ、３２ｂ用の制御
信号発生装置４０ａ、４０ｂの出力制御信号量と合流を
要するアクチュエータ１２ａ、１２ｂ用の制御信号発生
装置２０ａ、２０ｂの出力制御信号量との合計となる合
計出力制御信号量が、ポンプ５６の最大吐出流量を越え
た時に、この最大吐出量に対応する出力制御信号量を、
流量調整弁６６に出力する。そして、前記合計出力制御
信号量によって開度を調整された前記流量調整弁６４．
６６のそれぞれ前後の圧力が、前記ポンプ５４．５６の
制御部に印加され、これによりポンプ吐出流星が所定の
流量に設定される。20b and 40a, 40b, flow rate regulating valves 64.66 are provided through control calculation devices 60.62, respectively. Note that the control calculation device 60 is the composite control valve 50.
The output control signal amount of the control signal generators 20a, 20b for the actuators 12a, 12b and the composite control valve 5 in
Actuators 32a, 32b that require merging at 2
When the total output control signal amount, which is the sum of the output control signal amounts of the control signal generators 40a and 40b, exceeds the maximum discharge flow rate of the pump 54, the output control signal amount corresponding to this maximum discharge amount is , is output to the flow rate adjustment valve 64. The control calculation device 62 calculates the sum of the output control signal amount of the control signal generators 40a, 40b for the actuators 32a, 32b and the output control signal amount of the control signal generators 20a, 20b for the actuators 12a, 12b that require merging. When the total output control signal amount exceeds the maximum discharge flow rate of the pump 56, the output control signal amount corresponding to this maximum discharge amount is
It is output to the flow rate adjustment valve 66. The flow rate regulating valve 64 whose opening degree is adjusted according to the total output control signal amount.
66 pressures are applied to the control of the pumps 54, 56, thereby setting the pump discharge meteor to a predetermined flow rate.
また、連通弁５８はブロック型に形成され、その一端部
にアクチュエータ１２ｂ用の制御信号発生装置２０ｂが
らの制御信号が印加され、他端部にアクチュエータ３２
ａ ３２ｂ用の制御信号発生装置４０ａ、４０ｂがら
の制御信号の中でその大きい方の信号量が制御装置６８
を介して印加される。なお、連通弁は、第２図に示すよ
うな絞り型連通弁７０に形成しても良い。そして、この
連通弁５８あるいは７０は、その両端部に印加される制
御信号の双方の信号量が略等しいかもしくは共に作用し
ていない際には、両複合制御制御弁５０．５２の間をブ
ロックもしくは絞りを介して連通し、一方前記制御信号
の双方の信号量が異なるかもしくは一方のみが作用して
いる際には、両複合制御弁５０．５２の間を連通ずる。Further, the communication valve 58 is formed in a block shape, and a control signal from the control signal generator 20b for the actuator 12b is applied to one end thereof, and a control signal from the control signal generator 20b for the actuator 12b is applied to the other end.
The larger signal amount of the control signals from the control signal generators 40a and 40b for a 32b is the control signal generator 68.
applied via. Note that the communication valve may be formed as a throttle type communication valve 70 as shown in FIG. When the signal amounts of the control signals applied to both ends of the communication valve 58 or 70 are approximately equal or do not act together, the communication valve 58 or 70 blocks the connection between the two composite control valves 50 and 52. Otherwise, they communicate through a throttle, and when the amounts of both of the control signals are different or only one of them is acting, communication is established between the two composite control valves 50 and 52.
次に、このような構成になる本発明の油圧流量制御装置
の作動について説明する。Next, the operation of the hydraulic flow control device of the present invention having such a configuration will be explained.
先ず、両複合制御弁５０．５２におけるそれぞれ大流量
側のアーム用アクチュエータ１２ｂあるいはブーム用ア
クチュエータ３２ａを、単独ですなわち例えはブーム用
アクチュエータ３２ａのみを駆動する際は、このアクチ
ュエータ３２ａ用の制御信号発生装置４０ａが操作され
る。すると、この制御信号発生装置４０ａから出力され
る制御信号により、方向切換弁３４ａが切換えられると
共に、前記制御信号の信号量に対応して制御演算装置６
２によって設定される流量指令値が流量調整弁６６に印
加され、ポンプ５６から吐出される所定量の圧油かアク
チュエータ３２ａに供給される。更に、前記制御信号に
よって連通弁５８が連通されると共に、前記信号量に対
応して制御演算装置６０によって設定される流量指令値
が流量調整弁６４に印加され、ポンプ５４から吐出され
る所定量の圧油がポンプ５６からの圧油に合流されてア
クチュエータ３２ａに供給される。このようにして、ア
クチュエータ３２ａは、両ポンプ５４．５６からの合流
された圧油流量によって所定の速度で駆動される。なお
、アーム用アクチュエータ１２ｂも同様にして華独駆動
される。First, when driving the arm actuator 12b or boom actuator 32a on the large flow side of both composite control valves 50, 52 alone, for example, only the boom actuator 32a, a control signal for this actuator 32a is generated. Device 40a is operated. Then, the direction switching valve 34a is switched by the control signal output from the control signal generator 40a, and the control calculation device 6 is switched in accordance with the signal amount of the control signal.
2 is applied to the flow rate adjustment valve 66, and a predetermined amount of pressure oil discharged from the pump 56 is supplied to the actuator 32a. Furthermore, the communication valve 58 is communicated with the control signal, and a flow rate command value set by the control calculation device 60 corresponding to the signal amount is applied to the flow rate adjustment valve 64, thereby adjusting the predetermined amount discharged from the pump 54. The pressure oil is combined with the pressure oil from the pump 56 and supplied to the actuator 32a. In this way, the actuator 32a is driven at a predetermined speed by the combined pressure oil flow from both pumps 54,56. Note that the arm actuator 12b is also driven in the same manner.
次に、大流量の両アクチュエータ１２ｂ。Next, both large flow actuators 12b.
３２ａを同時にしかも高速駆動すべくそれぞれの制御信
号発生装置２０ｂ、４０ａを共に最大量操作した場合に
は、ポンプ５４．５６はそれぞれの制御演算装置６０．
６２並びに流量調整弁６４．６６を介して最大吐出流量
に設定される。しかるに、この場合、連通弁５８は、そ
の両端部に等しい大きさの制御信号量を作用されるので
ブロック位置となり、両複合制御弁５０．５２間の連通
が遮断される。従って、両アクヂュエータ１２ｂ。When the respective control signal generators 20b, 40a are both operated by the maximum amount in order to simultaneously drive the pumps 54, 56 and 32a at high speed, the respective control signal generators 60.
62 as well as flow rate regulating valves 64 and 66 to set the maximum discharge flow rate. However, in this case, the communication valve 58 is applied with the same amount of control signal to both ends thereof, so it is in the blocked position, and communication between the two composite control valves 50 and 52 is cut off. Therefore, both actuators 12b.
３２ａはそれぞれのポンプ５４．．５６の各最大吐出量
によって個別単独的に駆動される。32a are respective pumps 54. ．． Each of the 56 maximum discharge amounts is individually driven.
このように、本発明の油圧流量制御装置においては、大
容量の両アクチュエータ１２ｂ。In this way, in the hydraulic flow control device of the present invention, both large-capacity actuators 12b.
３２ａを同時に高速駆動しようとした場合でも、その駆
動速度は単独操作時の略半分になるとはいえ、従来の装
置におけるように、負荷が大きい側のアクチュエータの
作動を停止させるような不都合は発生しない。なおこの
場合、制御信号発生装置２０ｂ、４０ａの何れか一方の
制御操作量を減じると、ずなわち例えは装置４０ａの操
作レバーを中立方向へ少し戻すと、連通弁５８は絞りお
よびチエツクを介して両複合制御弁５０．５２間を連通
し、ポンプ５６の吐出流量の一部かアクチュエータ１２
ｂに供給される。従って、アクチュエータ３２ａの速度
が幾分減少され、一方この減少速度分たけアクチュエー
タ１２ｂの速度が増大される。また同様に、装置２０ｂ
の制御操作量を減じると、アクチュエータ１２ｂの速度
が幾分減少され、この減少速度分たけアクチュエータ３
２ａの速度が増大される。なお、この場合、アクチュエ
ータの駆動負荷は、ブーム用アクチュエータ３２ａ３の
方が通常大きいので、ポンプ吐出圧力はポンプ５６の方
が高圧に設定されているが、連通弁５８．７０にはチエ
ツクが介装されているので、ポンプ吐出圧油が逆流され
ることはない。すなわち、連通弁の連通により、ポンプ
５６からの吐出圧油がアクチュエータ１．２ ｂに逆に
供給されて、制御操作とは逆にアクチユエータ１．２
ｂが増速されるという不都合は発生されることがない。Even if you try to drive 32a at high speed at the same time, the drive speed will be approximately half of that when operated alone, but unlike conventional devices, there will be no inconvenience such as stopping the operation of the actuator on the side with a larger load. . In this case, if the control operation amount of either one of the control signal generators 20b and 40a is reduced, for example, if the operating lever of the device 40a is slightly returned to the neutral direction, the communication valve 58 will be closed via the throttle and check. A portion of the discharge flow rate of the pump 56 or the actuator 12 is communicated between the two composite control valves 50 and 52.
b. Therefore, the speed of actuator 32a is reduced somewhat, while the speed of actuator 12b is increased by this reduced speed. Similarly, the device 20b
When the control operation amount is reduced, the speed of the actuator 12b is somewhat reduced, and the actuator 3
The speed of 2a is increased. In this case, since the actuator driving load is normally larger for the boom actuator 32a3, the pump discharge pressure is set to a higher pressure for the pump 56, but a check is installed in the communication valve 58.70. Therefore, the pump discharge pressure oil will not flow backwards. That is, due to the communication of the communication valve, the discharge pressure oil from the pump 56 is supplied to the actuator 1.2b in the opposite direction to the control operation.
The inconvenience of speeding up b does not occur.
次に、複合制御弁５２における小流量のバケツＩ−用ア
クチュエータ３２の駆動速度を、他方のポンプ５４の吐
出圧油を合流させて、例えは１．５速に増速する際には
、制御信号発生装置４０ｂの制御信号量が、制御演算装
置６０によって１／２に減少された上で流量調整弁６４
に出力される。これによって、ポンプ５４は０．５速に
相当する吐出流量を増大され、この増大吐出圧油が連通
弁５８を介してアクチュエータ３２ｂに合流供給される
。Next, when increasing the driving speed of the small flow bucket I actuator 32 in the compound control valve 52 to, for example, 1.5 speed by merging the discharge pressure oil of the other pump 54, control is performed. After the control signal amount of the signal generator 40b is reduced to 1/2 by the control calculation device 60, the flow rate adjustment valve 64
is output to. As a result, the discharge flow rate of the pump 54 corresponding to 0.5 speed is increased, and this increased discharge pressure oil is combined and supplied to the actuator 32b via the communication valve 58.
従って、アクチュエータ３２ｂは制御操作値の１，５速
で駆動される。このように、本発明の油圧流量制御装置
においては、合流される１則のポンプの吐出流量をこの
ポンプの最大吐出流量の範囲内において任意所定に設定
することができる。従って、アクチュエータの運転精度
並びに装置の運転効率を向上することができる。Therefore, the actuator 32b is driven at the 1st and 5th speeds of the control operation value. As described above, in the hydraulic flow rate control device of the present invention, the discharge flow rates of the combined pumps can be arbitrarily set within the range of the maximum discharge flow rates of the pumps. Therefore, the operating accuracy of the actuator and the operating efficiency of the device can be improved.
なお、圧力補償弁１８ａ、１８ｂ、３８ａ。Note that the pressure compensation valves 18a, 18b, and 38a.
３８ｂは取除いても良く、第３図の実施例はこのような
実施態様を示したものである。38b may be removed, and the embodiment of FIG. 3 illustrates such an embodiment.
以上、本発明を好適な実施例について説明しなか、本発
明はその精神を逸脱することなく多くの設計変更をなし
得ることは勿論である。Although the present invention has been described above with reference to preferred embodiments, it goes without saying that the present invention can be modified in many ways without departing from its spirit.
以上説明したように、本発明に係る建設機械の油圧流量
制御装置は、各々に少くともアクチュエータを操作する
ための２つの方向切換弁を有する一対の複合制御弁と、
これら複合制御弁の各々にそれぞれ圧油を供給する一対
の可変容量ポンプと、前記方向切換弁の操作量をそれぞ
れ制御する複数の制御信号発生装置と、前記一対の複合
制御弁の間を相互に連通ずる連通弁とからなる油圧流量
制御装置において、
前記複合制御弁をクローズドセンタ型とし、前記可変容
量ポンプを負荷感応制御型とし、前記複合制御弁と前記
負荷感応制御型可変容量ポンプとの間に流量調整弁を設
け、前記制御信号発生装置の制御信号および／もしくは
制御Ｉ信号量で前記連通弁を開閉すると共に、前記制御
信号発生装置の制御信号量で前記流量調整弁の開度を調
整してこの流量調整弁の前後の圧力を前記負荷感応制御
型可変容量ポンプの制御部に印加するよう構成したので
、互いに相手側のポンプ吐出流量を合流させて増速駆動
される両アクチュエータを同時に最大増速操作した際に
も、この両アクチュエータをその負荷の如何にかかわら
ず同時に駆動することができる。また、必要合流量がポ
ンプ吐出流量の最大流量に達しない際には前記合流量を
任意所定の必要量に規定することができる。As explained above, the hydraulic flow control device for construction machinery according to the present invention includes a pair of compound control valves each having at least two directional control valves for operating at least an actuator;
A pair of variable capacity pumps that supply pressure oil to each of these composite control valves, a plurality of control signal generators that respectively control the operation amount of the directional control valve, and a mutual connection between the pair of composite control valves. A hydraulic flow control device comprising a sliding communication valve, wherein the composite control valve is of a closed center type, the variable displacement pump is of a load sensitive control type, and a gap between the composite control valve and the load sensitive variable displacement pump is A flow rate adjustment valve is provided in the control signal generator, and the communication valve is opened and closed by the control signal and/or control I signal amount of the control signal generator, and the opening degree of the flow rate adjustment valve is adjusted by the control signal amount of the control signal generator. Since the pressure before and after the flow rate adjustment valve is applied to the control section of the load-sensitive variable displacement pump, the discharge flow rates of the pumps on the other side are combined to simultaneously drive both actuators to be driven at increased speed. Even when the maximum speed is increased, both actuators can be driven simultaneously regardless of their loads. Further, when the required flow rate does not reach the maximum flow rate of the pump discharge flow rate, the flow rate can be set to an arbitrary predetermined required amount.
従って、アクチュエータの操作性、安全性並びに運転効
率を向上することができる。Therefore, the operability, safety, and operating efficiency of the actuator can be improved.
第１図は本発明に係る建設機械の油圧流量制御装置の一
実施例を示す油圧回路図、第２図は第１図に示す油圧流
量制御装置におりる連通弁の別の実施例を示す油圧記号
、第３図は本発明に係る建設機械の油圧流量制御装置の
別の実施例を示す油圧回路図、第４図は従来の建設機械
の油圧流量制御装置を示す油圧回路図である。
５０．５２
５４．５６
５８．７０
６４．６６
・・・複合制御弁
・・・負荷感応制御型可変容量ポンプ
・・連通弁 ６０．６２・・・制御演算装置・・・
流量調整弁 ６８・・・制御装置１ つFig. 1 is a hydraulic circuit diagram showing one embodiment of the hydraulic flow control device for construction machinery according to the present invention, and Fig. 2 shows another embodiment of the communication valve included in the hydraulic flow control device shown in Fig. 1. 3 is a hydraulic circuit diagram showing another embodiment of the hydraulic flow control device for construction machinery according to the present invention, and FIG. 4 is a hydraulic circuit diagram showing a conventional hydraulic flow control device for construction machinery. 50.52 54.56 58.70 64.66...Complex control valve...Load sensitive control type variable displacement pump...Communication valve 60.62...Control calculation unit...
Flow rate adjustment valve 68...1 control device
Claims (5)
の２つの方向切換弁を有する一対の複合制御弁と、これ
ら複合制御弁の各々にそれぞれ圧油を供給する一対の可
変容量ポンプと、前記方向切換弁の操作量をそれぞれ制
御する複数の制御信号発生装置と、前記一対の複合制御
弁の間を相互に連通する連通弁とからなる油圧流量制御
装置において、 前記複合制御弁をクローズドセンタ型とし、前記可変容
量ポンプを負荷感応制御型とし、前記複合制御弁と前記
負荷感応制御型可変容量ポンプとの間に流量調整弁を設
け、前記制御信号発生装置の制御信号および／もしくは
制御信号量で前記連通弁を開閉すると共に、前記制御信
号発生装置の制御信号量で前記流量調整弁の開度を調整
してこの流量調整弁の前後の圧力を前記負荷感応制御型
可変容量ポンプの制御部に印加するよう構成することを
特徴とする建設機械の油圧流量制御装置。(1) A pair of compound control valves each having two directional control valves for operating at least an actuator, a pair of variable displacement pumps that respectively supply pressure oil to each of these compound control valves, and A hydraulic flow control device comprising a plurality of control signal generators each controlling the operation amount of a valve, and a communication valve communicating between the pair of compound control valves, wherein the compound control valve is a closed center type, The variable displacement pump is of a load-sensitive control type, and a flow rate adjustment valve is provided between the composite control valve and the load-sensitive control type variable displacement pump, and the control signal and/or control signal amount of the control signal generator is used to control the amount of the control signal. At the same time as opening and closing the communication valve, the opening degree of the flow rate adjustment valve is adjusted by the control signal amount of the control signal generator, and the pressure before and after the flow rate adjustment valve is applied to the control unit of the load sensitive control type variable displacement pump. A hydraulic flow control device for construction machinery, characterized in that it is configured to.
制御信号が互いに対向して印加され、前記制御信号の双
方の信号量が略等しいかもしくは共に作用していない際
には前記両複合制御弁の間をブロックするかもしくは絞
りを介して連通し、前記制御信号の双方の信号量が異な
るかもしくは一方のみが作用している際には両複合制御
弁の間を連通するよう構成してなる請求項１記載の建設
機械の油圧流量制御装置。(2) When the control signals of the directional control valves in the two composite control valves are applied opposite to each other, and the signal amounts of both of the control signals are approximately equal or do not act together, the communication valve The control valves are blocked or communicated through a throttle, and when the signal amounts of both of the control signals are different or only one of them is acting, the two composite control valves are configured to communicate. 2. A hydraulic flow control device for construction machinery according to claim 1.
生装置の操作により、連通弁は両複合制御弁の間を連通
し、前記特定の方向切換弁を含まない側の複合制御弁に
接続された負荷感応制御型可変容量ポンプはそのポンプ
吐出流量をポンプ最大吐出流量以下の任意の流量に規制
されるよう構成してなる請求項１記載の建設機械の油圧
流量制御装置。(3) By operating a predetermined control signal generator for a specific directional switching valve, the communication valve communicates between the two composite control valves and connects to the composite control valve on the side that does not include the specific directional switching valve. 2. The hydraulic flow rate control device for construction machinery according to claim 1, wherein the load-sensitive variable displacement pump is configured such that its pump discharge flow rate is regulated to an arbitrary flow rate less than or equal to the pump maximum discharge flow rate.
請求項１記載の建設機械の油圧流量制御装置。(4) The hydraulic flow control device for construction machinery according to claim 1, wherein the directional switching valve of the composite control valve has a pressure compensation valve.
い請求項１記載の建設機械の油圧流量制御装置。(5) The hydraulic flow control device for construction machinery according to claim 1, wherein the directional switching valve of the composite control valve does not have a pressure compensation valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1032884A JP2776868B2 (en) | 1989-02-14 | 1989-02-14 | Hydraulic flow control device for construction machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1032884A JP2776868B2 (en) | 1989-02-14 | 1989-02-14 | Hydraulic flow control device for construction machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02212606A true JPH02212606A (en) | 1990-08-23 |
| JP2776868B2 JP2776868B2 (en) | 1998-07-16 |
Family
ID=12371301
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1032884A Expired - Lifetime JP2776868B2 (en) | 1989-02-14 | 1989-02-14 | Hydraulic flow control device for construction machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2776868B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1992009811A1 (en) * | 1990-11-27 | 1992-06-11 | Kabushiki Kaisha Komatsu Seisakusho | Stream separating or combining change-over system of a plurality of pumps in load sensing system |
| JP2007032790A (en) * | 2005-07-29 | 2007-02-08 | Shin Caterpillar Mitsubishi Ltd | Fluid pressure controller, fluid pressure control method, and hydraulic controller |
| CN102261351A (en) * | 2010-05-24 | 2011-11-30 | 上海三一科技有限公司 | Simple proportional load sensitive hydraulic system |
| JP2014058188A (en) * | 2012-09-14 | 2014-04-03 | Sumitomo (Shi) Construction Machinery Co Ltd | Hydraulic drive type power generation device |
| CN110848190A (en) * | 2019-09-25 | 2020-02-28 | 张家口凯航液压科技有限公司 | Integrated load sensitive flow divider valve |
-
1989
- 1989-02-14 JP JP1032884A patent/JP2776868B2/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1992009811A1 (en) * | 1990-11-27 | 1992-06-11 | Kabushiki Kaisha Komatsu Seisakusho | Stream separating or combining change-over system of a plurality of pumps in load sensing system |
| JP2007032790A (en) * | 2005-07-29 | 2007-02-08 | Shin Caterpillar Mitsubishi Ltd | Fluid pressure controller, fluid pressure control method, and hydraulic controller |
| CN102261351A (en) * | 2010-05-24 | 2011-11-30 | 上海三一科技有限公司 | Simple proportional load sensitive hydraulic system |
| JP2014058188A (en) * | 2012-09-14 | 2014-04-03 | Sumitomo (Shi) Construction Machinery Co Ltd | Hydraulic drive type power generation device |
| CN110848190A (en) * | 2019-09-25 | 2020-02-28 | 张家口凯航液压科技有限公司 | Integrated load sensitive flow divider valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2776868B2 (en) | 1998-07-16 |
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