JPH0467037B2 - - Google Patents
Info
- Publication number
- JPH0467037B2 JPH0467037B2 JP24842886A JP24842886A JPH0467037B2 JP H0467037 B2 JPH0467037 B2 JP H0467037B2 JP 24842886 A JP24842886 A JP 24842886A JP 24842886 A JP24842886 A JP 24842886A JP H0467037 B2 JPH0467037 B2 JP H0467037B2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic pump
- pipe
- switching valve
- motor
- valve
- 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.)
- Expired
Links
- 238000012360 testing method Methods 0.000 claims description 25
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 230000007935 neutral effect Effects 0.000 claims description 6
- 238000010586 diagram Methods 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Description
【発明の詳細な説明】
本発明は、例えば建設機械の油圧ポンプ、油圧
トランスミツシヨン、トルクコンバータ、油圧モ
ータ等の各種供試油圧機器の性能、調整試験用駆
動及び負荷装置に関し、油圧ポンプモータを駆動
油圧モータ及び負荷油圧ポンプとして兼用させた
ものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a drive and load device for performance and adjustment testing of various hydraulic equipment under test, such as hydraulic pumps, hydraulic transmissions, torque converters, and hydraulic motors for construction machinery. This is used both as a drive hydraulic motor and a load hydraulic pump.
（発明の技術的背景とその問題点）
油圧ポンプモータは、主油圧ポンプの吐出油に
よつて駆動モータとして機能する構造になつてお
り、該油圧ポンプモータを負荷油圧ポンプとして
働かせる場合、該負荷油圧ポンプの吸込部にはリ
ザーバから油を吸込み得る構造になつていないの
で、該負荷油圧ポンプの吸込み部に油を供給する
サブ油圧ポンプが必要である。(Technical background of the invention and its problems) A hydraulic pump motor has a structure in which it functions as a drive motor by the oil discharged from the main hydraulic pump, and when the hydraulic pump motor is used as a load hydraulic pump, the load Since the suction portion of the hydraulic pump does not have a structure capable of sucking oil from the reservoir, a sub-hydraulic pump is required to supply oil to the suction portion of the load hydraulic pump.
しかしながら、このようなサブ油圧ポンプを設
置しておくことは設備上不経済であるばかりか、
その分広いスペースを必要とし、しかも構造が複
雑になるという不都合がある。 However, installing such a sub-hydraulic pump is not only uneconomical in terms of equipment, but also
This has the disadvantage that it requires a larger space and has a more complicated structure.
また、油圧ポンプモータを負荷油圧ポンプとし
て使用する場合は、供試油圧モータが一般に正、
逆回転両用であるので供試油圧モータをどちらに
回転されてもいいような構造が望ましい。 In addition, when using a hydraulic pump motor as a load hydraulic pump, the test hydraulic motor is generally
It is desirable to have a structure in which the test hydraulic motor can be rotated in either direction since it can be used for both reverse rotation.
特に操作員が供給油圧モータの回転方向を見て
切換弁作業を行うやり方は間違い易く危険であ
り、負荷油圧ポンプが供試油圧モータの回転方向
に自動追従されるのが好ましい。 In particular, the method in which the operator performs the switching valve operation by looking at the rotational direction of the supply hydraulic motor is easy to make mistakes and is dangerous, so it is preferable that the load hydraulic pump automatically follows the rotational direction of the test hydraulic motor.
（発明の概要）
本発明は、４ポート３位置切換弁の位置切換弁
により主油圧ポンプからの吐出油が循環管路を介
し油圧ポンプモータを回転させる駆動油圧ポンプ
モータとして使用され、また前記油圧ポンプモー
タを負荷油圧ポンプとして作動させる場合は、前
記切換弁が中立位置にあつて中間管路各分岐管の
チエツク弁を介して中間管路の高圧リリーフ弁か
ら負荷油圧ポンプの吐出部までの管路を高圧にし
て所定の負荷を働かせると共に前記中間位置の切
換弁センターポートを介して中間管路に流入する
主油圧ポンプからの吐出油を低圧リリーフ弁で圧
力調整して各バイパス管路のチエツク弁を介して
負荷油圧ポンプの吸込部に供給し、負荷油圧ポン
プが供試油圧モータの回転方向に自動追従し得る
ようにしたものである。(Summary of the Invention) The present invention provides a four-port three-position switching valve in which oil discharged from a main hydraulic pump is used as a drive hydraulic pump motor to rotate a hydraulic pump motor via a circulation pipe, and the hydraulic When the pump motor is operated as a load hydraulic pump, the switching valve is in the neutral position and the pipes from the high pressure relief valve of the intermediate pipe to the discharge part of the load hydraulic pump are connected via the check valves of each branch pipe of the intermediate pipe. Each bypass pipe is checked by applying a predetermined load to the pipe by applying a high pressure to the pipe and adjusting the pressure of the oil discharged from the main hydraulic pump flowing into the intermediate pipe via the center port of the switching valve at the intermediate position using a low-pressure relief valve. It is supplied to the suction section of the load hydraulic pump through a valve, so that the load hydraulic pump can automatically follow the rotational direction of the test hydraulic motor.
（実施例）
図面は本発明の一実施例を示し、第１図及び第
２図は油圧ポンプモータを駆動油圧モータとして
使用し、第３図及び第４図は仝上油圧ポンプモー
タを負荷油圧ポンプとして使用する例である。(Embodiment) The drawings show an embodiment of the present invention, in which the hydraulic pump motor is used as a drive hydraulic motor in FIGS. 1 and 2, and the hydraulic pump motor is used as a drive hydraulic motor in FIGS. 3 and 4. This is an example of using it as a pump.
図中１は、可変容量型主油圧ポンプで、モータ
又はエンジン２により回転駆動されることによつ
て吸込管３を介してリザーバ４より油を吸込み、
吐出管５より吐出させる例えば可変容量型アキシ
ヤルピストン油圧ポンプが使用される。６は、４
ポート３位置切換弁で、センターポート７を有す
る。８は、可変容量型油圧ポンプモータで、各種
供試油圧機器２２又は２３の被駆動軸２２ａ又は
駆動軸２３ａと連結されて駆動油圧モータ８′又
は負荷油圧ポンプ８″として兼用されるものであ
つて、例えば主油圧ポンプ１と同様構造の可変容
量型アキシヤルピストン油圧ポンプモータが使用
される。９ａ，９ｂは循環管路、１０ａ，１０ｂ
は圧力計である。各循環管路９ａ，９ｂの一端は
油圧ポンプモータ８の給、排油口に夫々接続さ
れ、他端が切換弁６のＡ、Ｂポートに夫々接続さ
れる。１１は、中間管路で、一端が前記中立位置
の切換弁センターポート７を介して主油圧ポンプ
１の吐出管５に接続されると共に切換弁６側から
順次低圧リリーフ弁１２、遠隔制御弁１３ａ付き
高圧リリーフ弁１３及び流量計１４が介装され
る。１１ａ，１１ｂは、中間管路他端を二つに分
岐させた分岐管で、各循環管路９ａ，９ｂに夫々
接続される。１５ａ，１５ｂは、も中間管路分岐
管１１ａ，１１ｂに夫々介装されたチエツク弁
で、各循環管路９ａ，９ｂから各分岐管１１ａ，
１１ｂへの流動のみを許すものである。なお、各
圧力計１０ａ，１０ｂは、中間管路各分岐管１１
ａ，１１ｂと各循環管路９ａ，９ｂとの夫々の接
続部１６ａ，１６ｂに設けられている。１７ａ，
１７ｂは、バイパス管路で、切換弁６と低圧リリ
ーフ弁１２間の中間管路１１を各循環管路に夫々
接続するものである。１８ａ，１８ｂは、各バイ
パス管路１７ａ，１７ｂに夫々介装されたチエツ
ク弁で、該各バイパス管路から各循環管路への流
動のみを許すものである。１９ａは切換弁６のＲ
ポートに接続された戻り管路、１９ｂは、低圧リ
リーフ弁１２と高圧リリーフ弁１３間の中間管路
１１に接続された戻り管路、１９ｃは、管路１９
ａ，１９ｂに接続された戻り管路でクーラ２０及
びフイルタ２１を介してリザーバ４に戻り油を還
流させる。 In the figure, 1 is a variable displacement main hydraulic pump, which sucks oil from a reservoir 4 through a suction pipe 3 by being rotationally driven by a motor or an engine 2.
For example, a variable displacement axial piston hydraulic pump is used to discharge from the discharge pipe 5. 6 is 4
This is a 3-position port switching valve with a center port 7. Reference numeral 8 denotes a variable displacement hydraulic pump motor, which is connected to the driven shaft 22a or drive shaft 23a of the various hydraulic equipment 22 or 23 under test and is also used as a drive hydraulic motor 8' or a load hydraulic pump 8''. For example, a variable displacement axial piston hydraulic pump motor having the same structure as the main hydraulic pump 1 is used.9a, 9b are circulation pipes, 10a, 10b
is a pressure gauge. One end of each circulation pipe 9a, 9b is connected to the oil supply and drain ports of the hydraulic pump motor 8, respectively, and the other end is connected to the A and B ports of the switching valve 6, respectively. Reference numeral 11 denotes an intermediate pipe, one end of which is connected to the discharge pipe 5 of the main hydraulic pump 1 via the switching valve center port 7 in the neutral position, and sequentially from the switching valve 6 side a low pressure relief valve 12 and a remote control valve 13a. A high pressure relief valve 13 and a flow meter 14 are interposed. 11a and 11b are branch pipes in which the other end of the intermediate pipe is branched into two, which are connected to the circulation pipes 9a and 9b, respectively. Reference numerals 15a and 15b indicate check valves interposed in the intermediate pipe branch pipes 11a and 11b, respectively, so that the respective branch pipes 11a and 15b are connected to the respective circulation pipes 9a and 9b.
This allows only flow to 11b. In addition, each pressure gauge 10a, 10b is connected to each intermediate pipe and each branch pipe 11.
a, 11b and the respective connection portions 16a, 16b of the circulation pipes 9a, 9b. 17a,
Reference numeral 17b denotes a bypass pipe, which connects the intermediate pipe 11 between the switching valve 6 and the low pressure relief valve 12 to each circulation pipe. Reference numerals 18a and 18b are check valves installed in the bypass pipes 17a and 17b, respectively, which allow flow only from the bypass pipes to the circulation pipes. 19a is R of the switching valve 6
The return line 19b is connected to the port, and the return line 19c is connected to the intermediate line 11 between the low pressure relief valve 12 and the high pressure relief valve 13.
The oil is returned to the reservoir 4 via the cooler 20 and the filter 21 in the return pipe line connected to the pipes a and 19b, and is refluxed.
次に、上記装置の作動を説明する。まず、第１
図及び第２図に示すように供試品が例えば油圧ポ
ンプ２２であつて油圧ポンプモータ８を駆動油圧
モータ８′として使用する場合を説明すると、供
試油圧ポンプ２２の被駆動軸２２ａを駆動油圧モ
ータ８′の回転軸８a′に連結すると共に高圧リリ
ーフ弁１３を最高圧力にセツトして主油圧ポンプ
１を始動すれば、主油圧ポンプ１からの吐出油が
切換弁６の両側位置切換弁により循環管路９ａ，
９ｂを矢視の如く流れて駆動油圧モータ８′を正
回転又は逆回転させ、該駆動油圧モータで運転さ
れる供試油圧ポンプ２２の性能、調整試験が公知
の油圧ポンプ試験装置（図示しない）により行わ
れる。この試験中、主油圧ポンプ１から駆動油圧
モータ８′に供給する油の圧力を一定（例えば15
Kgｆ／cm2）にしておく必要があるが、この圧力は
圧力計１０ａ又は１０ｂにより検出されて制御さ
れる。この場合、高圧リリーフ弁１３とチエツク
弁１８ａ，１８ｂの働きにより戻り管路１９ｂか
らの油の還流はない。なお、油圧ポンプモータ８
を駆動油圧モータ８′とした場合供試油圧機器と
しては、上記油圧ポンプの他、油圧トランスミツ
シヨン、トルクコンバータ等が適用できる。 Next, the operation of the above device will be explained. First, the first
As shown in FIG. 2 and FIG. 2, for example, the sample is a hydraulic pump 22 and the hydraulic pump motor 8 is used as a drive hydraulic motor 8'. When the main hydraulic pump 1 is started by connecting it to the rotating shaft 8a' of the hydraulic motor 8' and setting the high pressure relief valve 13 to the maximum pressure, the oil discharged from the main hydraulic pump 1 is transferred to the switching valve 6. The circulation pipe 9a,
A known hydraulic pump testing device (not shown) is used to test the performance and adjustment of the test hydraulic pump 22 operated by the hydraulic drive motor 8' by rotating the drive hydraulic motor 8' in the forward or reverse direction as shown by the arrow 9b. This is done by During this test, the pressure of the oil supplied from the main hydraulic pump 1 to the drive hydraulic motor 8' is kept constant (for example, 15
Kgf/cm 2 ), and this pressure is detected and controlled by the pressure gauge 10a or 10b. In this case, the high pressure relief valve 13 and the check valves 18a, 18b do not allow oil to flow back from the return pipe 19b. In addition, the hydraulic pump motor 8
When the drive hydraulic motor 8' is used as the drive hydraulic motor 8', the hydraulic equipment to be tested may include, in addition to the above-mentioned hydraulic pump, a hydraulic transmission, a torque converter, etc.
また、第３図及び第４図に示すように供試品が
油圧モータ２３であつて油圧ポンプモータ８を負
荷油圧ポンプ８″として使用する場合を説明する
と、供試油圧ポンプ２３の駆動軸２３ａを負荷油
圧ポンプ８″の回転軸８a″に連結すると共に切換
弁６を中立位置にセツトし、且つ低圧リリーフ弁
１２を例えば10〜12Kgｆ／cm2の範囲の任意の圧力
に調節設定すると共に高圧リリーフ弁１３を例え
ば21〜350Kgｆ／cm2の範囲の任意の圧力に調節設
定しおく。この状態で、主油圧ポンプ１を運転す
ると共に供試油圧モータ２３を始動すれば、該供
試油圧モータ２３により正回転又は逆回転された
負荷油圧ポンプ８″から循環管路９ａ又は９ｂに
吐出された圧油は、チエツク弁１５ａ又は１５ｂ
の働きにより第３図又は第４図矢視の如く自動的
に流れ方向を切換えられて中間管路１１に流れ込
み高圧リリーフ弁１３から負荷油圧ポンプ８″吐
出部までの管路が高圧リリーフ弁１３で該設定さ
れた高圧になることによつて生じる所定の流れ抵
抗（これが油圧ポンプ８″の負荷となり、この負
荷の程度は、高圧リリーフ弁１３の圧力調整によ
つて任意に設定される。）をかけられて戻り管路
１９ｂ，１９ｃを介してリザーバ４に還流される
と共に主油圧ポンプ１の吐出油は、中立位置の切
換弁センターポート７から中間管路１１に流入
し、低圧リリーフ弁１２で圧力調整されながら、
負荷油圧ポンプ８″の回転方向により該油圧ポン
プの吐出圧がかからない片方のバイパス管路のチ
エツク弁１８ｂ又は１８ａを開いて循環管路９ｂ
又は９ａを介して負荷油圧ポンプ８″の吸込部８
ｂに供給される。低圧リリーフ弁１２から流出す
る油は戻り管路１９ｂ，１９ｃを介してリザーバ
４に還流される。 Further, as shown in FIGS. 3 and 4, when the sample is a hydraulic motor 23 and the hydraulic pump motor 8 is used as a load hydraulic pump 8'', the drive shaft 23a of the sample hydraulic pump 23 is is connected to the rotary shaft 8a'' of the load hydraulic pump 8'', the switching valve 6 is set to the neutral position, and the low pressure relief valve 12 is adjusted to an arbitrary pressure in the range of, for example, 10 to 12 Kgf/ cm2 , and the high pressure The relief valve 13 is adjusted and set to an arbitrary pressure in the range of, for example, 21 to 350 Kgf/ cm2.In this state, if the main hydraulic pump 1 is operated and the test hydraulic motor 23 is started, the test hydraulic motor Pressure oil discharged into the circulation pipe 9a or 9b from the load hydraulic pump 8'' rotated forward or backward by the check valve 15a or 15b
The flow direction is automatically switched as shown by the arrow in FIG. A predetermined flow resistance caused by reaching the set high pressure (this becomes a load on the hydraulic pump 8'', and the degree of this load is arbitrarily set by adjusting the pressure of the high pressure relief valve 13). The oil discharged from the main hydraulic pump 1 flows into the intermediate pipe 11 from the switching valve center port 7 in the neutral position, and is returned to the reservoir 4 via the return pipes 19b and 19c. While the pressure is adjusted by
Depending on the direction of rotation of the load hydraulic pump 8'', the check valve 18b or 18a of the bypass line to which the discharge pressure of the hydraulic pump is not applied is opened, and the circulation line 9b is opened.
or the suction part 8 of the load hydraulic pump 8'' via 9a
b. Oil flowing out from the low pressure relief valve 12 is returned to the reservoir 4 via return pipes 19b and 19c.
そして、供試油圧モータ２３の回転方向が変わ
つた場合、チエツク弁１５ａ又は１５ｂの働きに
よつて負荷油圧ポンプ８″の吐出部に高圧を加え
る管路が自動的に切換えられ、主油圧ポンプ１か
らの吐出油も負荷油圧ポンプ８″の吐出圧がかか
らず軽く開くチエツク弁１８ｂ又は１８ａの働き
によつて自動的に流れ方向が切換えられるので、
負荷油圧ポンプ８″を供試油圧モータ２３の回転
方向に自動追従させることができる。圧力計１０
ａ又は１０ｂと流量計１４で圧力と流量を求めれ
ば、供試油圧モータの負荷の程度が解析でき、該
供試油圧モータの性能調整試験が公知の油圧モー
タ試験装置（図示しない）によつて行われる。こ
の場合、片方の圧力計により負荷油圧ポンプの吐
出部に加わる負荷圧を検出するたけでなく、他の
圧力計により主油圧ポンプから負荷油圧ポンプの
吸込部に供給される油の圧力も検出できる。ま
た、リザーバへの還流油をクーラによつて冷却し
て試験中の油の温度を一定に保つことによつて試
験の信頼性を向上できる。 When the rotation direction of the test hydraulic motor 23 changes, the check valve 15a or 15b automatically switches the line that applies high pressure to the discharge part of the load hydraulic pump 8'', and the main hydraulic pump 1 Since the discharge pressure from the load hydraulic pump 8'' is not applied to the oil discharged from the hydraulic pump 8'', the flow direction is automatically switched by the check valve 18b or 18a, which opens slightly.
The load hydraulic pump 8'' can automatically follow the rotational direction of the test hydraulic motor 23.The pressure gauge 10
By determining the pressure and flow rate using a or 10b and the flow meter 14, the degree of load on the test hydraulic motor can be analyzed, and the performance adjustment test of the test hydraulic motor can be performed using a known hydraulic motor testing device (not shown). It will be done. In this case, not only can one pressure gauge detect the load pressure applied to the discharge section of the load hydraulic pump, but the other pressure gauge can also detect the pressure of oil supplied from the main hydraulic pump to the suction section of the load hydraulic pump. . Furthermore, the reliability of the test can be improved by cooling the oil returned to the reservoir with a cooler to keep the temperature of the oil constant during the test.
（発明の効果）
本発明は以上説明したように、主油圧ポンプが
油圧ポンプモータを駆動油圧モータとして使用す
る場合の駆動ポンプとなるだけでなく、負荷油圧
ポンプとして使用する場合に該負荷油圧ポンプ吸
い込部に油を供給するサブ油圧ポンプの機能をも
兼用し、サブ油圧モータを別に設置するものに比
較してよりコンパクトで簡単な構成にできると共
に負荷油圧ポンプとして使用する場合に中間管路
分岐管のチエツク弁、高圧リリーフ弁、低圧リリ
ーフ弁及びバイパス管路のチエツク弁の働きによ
つて負荷油圧ポンプを供試油圧モータの回転方向
がいずれの方向であつても自動追従させることが
でき、従来のような操作ミスを起こす危険がな
い。(Effects of the Invention) As explained above, the present invention not only serves as a drive pump when the main hydraulic pump uses a hydraulic pump motor as a drive hydraulic motor, but also serves as a load hydraulic pump when used as a load hydraulic pump. It also functions as a sub-hydraulic pump that supplies oil to the suction section, allowing for a more compact and simpler configuration compared to systems that install a sub-hydraulic motor separately, and an intermediate pipe when used as a load hydraulic pump. By the function of the branch pipe check valve, high pressure relief valve, low pressure relief valve, and bypass pipe check valve, the load hydraulic pump can automatically follow the rotational direction of the test hydraulic motor. , there is no risk of making operational mistakes like in the past.
また、本発明において、中間管路各分岐管と各
循環管路との接続部に圧力計を設けておけば、循
環管路の圧力は勿論、高圧リリーフ弁から負荷油
圧ポンプ吐出部までの管路圧力をも正確に検出で
きる。 In addition, in the present invention, if a pressure gauge is provided at the connection between each branch pipe of the intermediate pipe and each circulation pipe, it is possible to check not only the pressure of the circulation pipe, but also the pressure of the pipe from the high pressure relief valve to the discharge part of the load hydraulic pump. Road pressure can also be detected accurately.
第１図及び第２図は油圧ポンプモータを駆動油
圧モータとして使用する本発明駆動装置の系統
図、第３図及び第４図は油圧ポンプモータを負荷
油圧モータとして使用する本発明負荷装置の系統
図である。
１……可変容量型主油圧ポンプ、６……４ポー
ト３位置切換弁、７……センターポート、８……
可変容量型油圧ポンプモータ、９ａ，９ｂ……循
環管路、１１……中間管路、１１ａ，１１ｂ……
中間管路分岐管、１２……低圧リリーフ、１３…
…高圧リリーフ、１７ａ，１７ｂ……バイパス管
路、２２，２３……供試油圧機器。
Figures 1 and 2 are system diagrams of a drive device of the present invention that uses a hydraulic pump motor as a drive hydraulic motor, and Figures 3 and 4 are system diagrams of a load device of the present invention that uses a hydraulic pump motor as a load hydraulic motor. It is a diagram. 1...Variable displacement main hydraulic pump, 6...4 port 3 position switching valve, 7...Center port, 8...
Variable displacement hydraulic pump motor, 9a, 9b...Circulation pipe line, 11...Intermediate pipe line, 11a, 11b...
Intermediate pipe branch pipe, 12...Low pressure relief, 13...
...High pressure relief, 17a, 17b...Bypass pipeline, 22, 23...Test hydraulic equipment.
Claims (1)
の吐出管にＰポートを接続させると共に中立位置
で前記吐出管と接続されるセンターポートを有す
る４ポート３位置切換弁と、供試油圧機器の被駆
動軸又は駆動軸と連結されて駆動油圧モータ又は
負荷油圧ポンプとして兼用される可変容量型油圧
ポンプモータと、該油圧ポンプモータの給、排油
口に一端が夫々接続されると共に他端が前記切換
弁のＡ、Ｂポートに夫々接続され且つ圧力計を
夫々備える循環管路と、一端が前記中立位置の切
換弁のセンターポートを介して前記主油圧ポンプ
の吐出管に接続されると共に該切換弁側から順次
低圧リリーフ弁、高圧リリーフ弁及び流量計が介
装され且つ他端が二つに分岐され該各分岐管が前
記各循環管路から各分岐管への流動のみを許すチ
エツク弁を介して前記各循環管路に夫々接続され
た中間管路と、前記切換弁と前記低圧リーフ弁間
の中間管路を前記各循環管路への流動のみを許す
チエツク弁を介して前記各循環管路に夫々接続さ
せるバイパス管路と、前記切換弁のＲポートに接
続され且つ前記低圧リリーフ弁と高圧リリーフ弁
間の中間管路に夫々接続された戻り管路とを具備
してなる油圧機器試験用駆動及び負荷装置。 ２ 前記戻り管路にクーラを介装してなる特許請
求の範囲第１項記載の装置。 ３ 前記圧力計を、前記中間管路各分岐管と前記
各循環管路との夫々の接続部に設けてなる特許請
求の範囲第１項又は第２項記載の装置。[Scope of Claims] 1. A variable displacement main hydraulic pump, and a 4-port 3-position switching valve having a P port connected to a discharge pipe of the main hydraulic pump and a center port connected to the discharge pipe at a neutral position. , a variable displacement hydraulic pump motor that is connected to the driven shaft or drive shaft of the test hydraulic equipment and used as a drive hydraulic motor or a load hydraulic pump, and one end connected to the oil supply and drain ports of the hydraulic pump motor, respectively. a circulation pipe whose other end is connected to the A and B ports of the switching valve and each has a pressure gauge, and a discharge pipe of the main hydraulic pump whose one end is connected to the center port of the switching valve in the neutral position. At the same time, a low pressure relief valve, a high pressure relief valve and a flow meter are interposed in order from the switching valve side, and the other end is branched into two, and each branch pipe connects each circulation pipe to each branch pipe. Intermediate pipes connected to each of the circulation pipes through check valves that only allow flow, and intermediate pipes between the switching valve and the low-pressure leaf valve that only allow flow to each of the circulation pipes. a bypass pipe connected to each of the circulation pipes via a valve; and a return pipe connected to the R port of the switching valve and to an intermediate pipe between the low pressure relief valve and the high pressure relief valve. A drive and load device for testing hydraulic equipment, comprising: 2. The device according to claim 1, wherein a cooler is interposed in the return pipe. 3. The device according to claim 1 or 2, wherein the pressure gauge is provided at each connection between each branch pipe of the intermediate pipe line and each circulation pipe line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24842886A JPS63105290A (en) | 1986-10-21 | 1986-10-21 | Driving and loading device for testing hydraulic equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24842886A JPS63105290A (en) | 1986-10-21 | 1986-10-21 | Driving and loading device for testing hydraulic equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63105290A JPS63105290A (en) | 1988-05-10 |
| JPH0467037B2 true JPH0467037B2 (en) | 1992-10-27 |
Family
ID=17177977
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24842886A Granted JPS63105290A (en) | 1986-10-21 | 1986-10-21 | Driving and loading device for testing hydraulic equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63105290A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014228016A (en) * | 2013-05-20 | 2014-12-08 | マルマテクニカ株式会社 | Hydraulic test device |
| KR20150087375A (en) | 2013-11-19 | 2015-07-29 | 가부시키가이샤 하모닉 드라이브 시스템즈 | Strain wave gear device, friction engagement type strain wave device, and wave generator |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4903529A (en) * | 1988-10-07 | 1990-02-27 | Westinghouse Electric Corp. | Valve system analyzer |
| CN102330717B (en) * | 2011-08-05 | 2012-12-19 | 三一重机有限公司 | Test system for hydraulic system of hydraulic excavator |
| CN102493954B (en) * | 2011-11-09 | 2014-04-30 | 中航力源液压股份有限公司 | On-line environment high-temperature test chamber for aviation kerosene hydraulic pump |
| JP5651099B2 (en) * | 2011-11-15 | 2015-01-07 | 日立建機株式会社 | Plunger pump failure diagnosis device |
| CN103711685A (en) * | 2012-09-29 | 2014-04-09 | 成都金福天下投资管理有限公司 | Hydraulic loading testing device |
| CN107727374B (en) * | 2017-05-05 | 2020-01-14 | 太原理工大学 | Simulation test bed for liquid conveying water valve of mine pipeline |
-
1986
- 1986-10-21 JP JP24842886A patent/JPS63105290A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014228016A (en) * | 2013-05-20 | 2014-12-08 | マルマテクニカ株式会社 | Hydraulic test device |
| KR20150087375A (en) | 2013-11-19 | 2015-07-29 | 가부시키가이샤 하모닉 드라이브 시스템즈 | Strain wave gear device, friction engagement type strain wave device, and wave generator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63105290A (en) | 1988-05-10 |
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