JPH0635844Y2 - Hydraulic retarder device - Google Patents
Hydraulic retarder deviceInfo
- Publication number
- JPH0635844Y2 JPH0635844Y2 JP10997387U JP10997387U JPH0635844Y2 JP H0635844 Y2 JPH0635844 Y2 JP H0635844Y2 JP 10997387 U JP10997387 U JP 10997387U JP 10997387 U JP10997387 U JP 10997387U JP H0635844 Y2 JPH0635844 Y2 JP H0635844Y2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- hydraulic
- retarder
- pressure
- hydraulic oil
- 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 - Lifetime
Links
Landscapes
- Transmission Of Braking Force In Braking Systems (AREA)
- Braking Arrangements (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） この考案は、例えば大型トラック等の車両の減速時に車
両の運動エネルギを吸収してサービスブレーキの負担を
軽減する補助ブレーキとして使用される油圧リターダ装
置に関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to a hydraulic retarder used as an auxiliary brake that absorbs kinetic energy of a vehicle such as a large truck to reduce the load on the service brake when the vehicle is decelerated. Regarding the device.
（従来の技術） 近年、大型トラック等の車両は、内燃エンジンに過給機
が装備される等により、高出力化、高速化の傾向にあ
り、これに伴い車両減速時により大きい制動力が必要に
なる傾向にある。車両の制動毎にサービスブレーキのみ
を使用して制動すると、制動の繰り返しによりブレーキ
がオーバヒートしたり、ブレーキシューライニングの摩
耗が激しく、短時間でライニングを交換する必要があ
る。従来、サービスブレーキの負担を軽減するために、
エンジンブレーキ、排気ブレーキ等の種々の補助ブレー
キ（リターダ装置）が使用されているが、上述の高出力
化、高速化に伴い、吸収馬力の大きいリターダ装置が要
請されている。(Prior Art) In recent years, vehicles such as heavy-duty trucks have tended to have higher output and higher speed due to a supercharger being installed in an internal combustion engine, which requires a larger braking force when decelerating the vehicle. Tends to become. When only the service brake is used for braking every time the vehicle is braked, the brake is overheated due to repeated braking and the brake shoe lining is severely worn, and it is necessary to replace the lining in a short time. Conventionally, in order to reduce the burden of service brakes,
Although various auxiliary brakes (retarder devices) such as engine brakes and exhaust brakes are used, a retarder device having a large absorption horsepower has been demanded with the above-described higher output and higher speed.
この要請に応えるものとして、ステータに対してロータ
を回転させることにより作動油に運動エネルギが放熱さ
れて吸引馬力を得る、流体式の油圧リターダ装置が、
「エンジンブレーキ補助装置の動向」自動車技術Vol.3
8,No.9,1984頁1067〜1074により知られている。このリ
ターダ装置は、第４図に示すように、ハウジング11と、
該ハウジング11側に固定されたステータ２と、回転軸、
例えば内燃エンジンのクランク軸10に固着されたロータ
３とで構成されるリターダ本体Ｒに加え、リターダ本体
Ｒに接続された作動油循環油路途中に配設され、運動エ
ネルギを吸収した作動油を冷却するオイルクーラ（第４
図には図示せず）と、作動油循環油路にオイル溜の作動
油を補給するオイルポンプ４とを備えており、オイルポ
ンプ４は、リターダ本体Ｒの作動時（吸収馬力取出時）
に作動油循環油路にオイル溜（第４図には図示せず）の
作動油を充填補給すると共に、作動油循環油路から低圧
側のオイル溜に漏れ出て不足する作動油を補給するもの
である。このオイルポンプ４はリターダ本体Ｒの非作動
時にオイル溜の作動油をオイルクーラに供給して作動油
を常時冷却する役割をも有している。尚、第４図におい
て、ステータ２とハウジング１間に挟装されるバルブボ
ディ５には、作動油循環油路途中に配設される切換弁等
を収容している。又、同図中符号６はロータ３の軸方向
スラスト力を受けるスラストベアリング、符号７は高圧
のロータ室９から作動油が低圧のシール室８に漏れ出る
のを防止するオイルリングである。In order to meet this demand, a fluid-type hydraulic retarder device that obtains suction horsepower by radiating kinetic energy to hydraulic oil by rotating a rotor with respect to a stator is provided.
"Trends of Engine Brake Auxiliary Device" Automotive Technology Vol.3
8, No. 9, pp. 1067-1074, 1984. This retarder device, as shown in FIG.
A stator 2 fixed to the housing 11 side, a rotating shaft,
For example, in addition to the retarder main body R composed of the rotor 3 fixed to the crankshaft 10 of the internal combustion engine, the hydraulic oil that is arranged in the hydraulic oil circulation oil passage connected to the retarder main body R and absorbs the kinetic energy Oil cooler for cooling (4th
(Not shown in the figure) and an oil pump 4 for replenishing the working oil in the oil reservoir to the working oil circulation oil passage. The oil pump 4 operates when the retarder body R is operating (when absorbing horsepower is taken out).
And replenish the hydraulic oil circulation oil passage with hydraulic oil from an oil reservoir (not shown in FIG. 4), and replenish the hydraulic oil that leaks from the hydraulic oil circulation oil passage to the low pressure side oil reservoir and runs short. It is a thing. The oil pump 4 also has a role of constantly supplying the working oil in the oil reservoir to the oil cooler when the retarder main body R is not working to cool the working oil. In FIG. 4, the valve body 5 sandwiched between the stator 2 and the housing 1 accommodates a switching valve or the like arranged in the working oil circulation oil passage. Further, in the figure, reference numeral 6 is a thrust bearing that receives the axial thrust force of the rotor 3, and reference numeral 7 is an oil ring that prevents hydraulic oil from leaking from the high pressure rotor chamber 9 to the low pressure seal chamber 8.
（考案が解決しようとする問題点） 斯かる従来の油圧リターダ装置において、リターダ本体
Ｒの作動時に作動油を作動油循環油路に押し込み補給す
るにはオイルポンプの吐出圧として４〜5kg/cm2の高圧
力が必要である一方、リターダ本体Ｒの非作動時に作動
油をオイルクーラに供給するには１〜2kg/cm2の低圧の
吐出圧で十分である。然るに、オイルポンプから吐出さ
れる作動油の吐出圧をリターダ本体Ｒの作動時に合わせ
て高圧の所定値に設定すると、リターダ本体Ｒの非作動
時にもこの設定圧でオイルクーラに作動油が供給される
ことになり、エンジンの出力がこのオイルポンプの駆動
のために無駄に使用されることになる。(Problems to be solved by the invention) In such a conventional hydraulic retarder device, when the retarder main body R is actuated, the working oil is pushed into the working oil circulation oil passage to supply the oil, the discharge pressure of the oil pump is 4 to 5 kg / cm. While a high pressure of 2 is required, a low discharge pressure of 1-2 kg / cm 2 is sufficient to supply hydraulic oil to the oil cooler when the retarder body R is not operating. However, if the discharge pressure of the hydraulic oil discharged from the oil pump is set to a predetermined high value in accordance with the operation of the retarder main body R, the hydraulic oil is supplied to the oil cooler at this set pressure even when the retarder main body R is not operating. Therefore, the output of the engine is wasted for driving the oil pump.
本考案は斯かる問題点を解決するためになされたもの
で、リターダ本体の非作動時にオイルポンプ駆動のため
の出力を最小限に抑え、フリクションロス（ポンピング
ロス）を極力小さくすると共に、オイルポンプの寿命の
延長を図った油圧リターダ装置を提供することを目的と
する。The present invention has been made to solve such a problem, and minimizes the output for driving the oil pump when the retarder body is not operating to minimize friction loss (pumping loss) and to reduce the oil pump. It is an object of the present invention to provide a hydraulic retarder device that extends the life of the device.
（問題点を解決するための手段） 上述の目的を達成するために本考案に依れば、ステータ
に対してロータを回転させることにより作動油に運動エ
ネルギが放熱されて吸収馬力を得るリターダ本体と、該
リターダ本体に接続された作動油循環油路途中に配設さ
れ、作動油を冷却するオイルクーラと、前記作動油循環
油路に作動油を補給するオイルポンプとを備える油圧リ
ターダ装置において、前記オイルポンプと前記作動油循
環油路間に該オイルポンプが吐出する作動油の吐出圧を
高低２段に切り換える油圧調整切換手段を配設すると共
に、前記作動油循環油路途中に、前記リターダ本体の作
動時に作動油を前記作動油循環油路を循環させ、非作動
時に前記リターダ本体内の作動油をオイル溜に排出させ
ると共に、前記オイルポンプから吐出される作動油を前
記オイルクーラを介して前記オイル溜に排出させる油路
切換手段を配設し、前記油圧調整切換手段は前記リター
ダ本体の作動時に作動油の吐出圧を高圧側に切り換え、
非作動時に低圧側に切り換えることを特徴とする油圧リ
ターダ装置が提供される。(Means for Solving the Problems) According to the present invention to achieve the above-mentioned object, according to the present invention, by rotating a rotor with respect to a stator, kinetic energy is radiated to hydraulic oil to obtain absorption horsepower. And a hydraulic retarder device provided with an oil cooler arranged midway in the hydraulic oil circulation oil passage connected to the retarder body, for cooling the hydraulic oil, and an oil pump for replenishing the hydraulic oil circulation oil passage with hydraulic oil. Between the oil pump and the hydraulic oil circulation oil passage, a hydraulic pressure adjustment switching means for switching the discharge pressure of the hydraulic oil discharged by the oil pump between high and low stages is provided, and in the middle of the hydraulic oil circulation oil passage, When the retarder main body is operating, the hydraulic oil is circulated in the hydraulic oil circulation oil passage, and when the retarder main body is not operating, the hydraulic oil in the retarder main body is discharged to the oil reservoir and discharged from the oil pump. Disposed is an oil passage switching means for discharging the operating oil to the oil reservoir via the oil cooler, and the hydraulic pressure adjustment switching means switches the discharge pressure of the operating oil to a high pressure side when the retarder main body operates.
There is provided a hydraulic retarder device characterized by switching to a low pressure side when not in operation.
（作用） 油圧調整切換手段によりリターダ本体の作動時に作動油
の吐出圧を高圧側に切り換え、非作動時に低圧側に切り
換えるために、オイルポンプから吐出される作動油の吐
出圧がリターダ本体の作動状態に応じて必要最適値に調
圧される。(Operation) The hydraulic pressure adjustment switching means changes the discharge pressure of the hydraulic oil to the high pressure side when the retarder main body operates, and switches to the low pressure side when the retarder main body does not operate. Therefore, the discharge pressure of the hydraulic oil discharged from the oil pump operates the retarder main body. The pressure is adjusted to the required optimum value according to the condition.
（実施例） 以下本考案の実施例を図面に基づいて詳細に説明する。(Embodiment) An embodiment of the present invention will be described in detail below with reference to the drawings.
第１図は本考案に係る油圧リターダ装置の油圧回路を示
し、第２図は本考案に係る油圧リターダ装置の取り付け
状態を示す。尚、これらの図面において、先に説明した
第４図と同一符号を付した構成要素はそれらのものと実
質的に同じものであるからこれらの詳細な説明は省略す
る。FIG. 1 shows a hydraulic circuit of a hydraulic retarder device according to the present invention, and FIG. 2 shows an attached state of the hydraulic retarder device according to the present invention. Note that, in these drawings, the constituent elements denoted by the same reference numerals as those in FIG. 4 described above are substantially the same as those elements, and thus detailed description thereof will be omitted.
油圧リターダ装置のリターダ本体Ｒはエンジン本体Ｅと
トランスミッションＴ間に介装され、第１図に示す油圧
回路は後述するオイルクーラ32,リザーバ34を除いて他
の構成要素は総てバルブボディ５内に収容されている。
リターダ本体Ｒのステータ２側に開口する排出孔2aには
油路12の一端が接続され、油路12の他端はコネクタ12a
を介して管路13の一端に接続されている。一方、リター
ダ本体Ｒのステータ２側に開口する吸入孔2bは油路14の
一端が接続され、油路14の他端はコネクタ14aを介して
管路13′の一端に接続されている。The retarder body R of the hydraulic retarder device is interposed between the engine body E and the transmission T, and the hydraulic circuit shown in FIG. 1 has all the other constituent elements inside the valve body 5 except for an oil cooler 32 and a reservoir 34 which will be described later. It is housed in.
One end of the oil passage 12 is connected to the discharge hole 2a opened to the stator 2 side of the retarder main body R, and the other end of the oil passage 12 is connected to the connector 12a.
Is connected to one end of the conduit 13 via. On the other hand, one end of the oil passage 14 is connected to the suction hole 2b of the retarder main body R that is open to the stator 2 side, and the other end of the oil passage 14 is connected to one end of the pipe passage 13 'through the connector 14a.
油路12には２個の３ポート２位置切換弁20,21が、油路1
4には１個のポート２位置切換弁22が夫々配設されてお
り、これらの切換弁20〜22は外部のパイロット圧、例え
ば空気圧により２位置に切り換えられる。即ち、後述す
るようにリターダ本体Ｒの非作動時には空気圧が何れの
切換弁にも供給されず、各切換弁20〜22は第１図に示す
第１の切換位置20A〜22Aの状態にあり、リターダ本体Ｒ
側及びコネクタ12a側の油路12はいずれもオイル溜30に
連通する油路に接続され、リターダ本体Ｒ側の油路14は
閉塞されると共に、コネクタ14a側の油路14は後述する
油路17の一端に接続される。一方、リターダ本体Ｒの作
動時には空気圧が総ての切換弁20〜22に供給され、各切
換弁20〜22は第２の切換位置20B〜22Bに切り換えられ、
リターダ本体Ｒの排出孔2aおよび吸入孔2bは油路12,13,
13′,14により接続されて作動油循環油路が形成され
る。Two 3-port 2-position changeover valves 20, 21 are provided in the oil passage 12
The port 4 is provided with one port 2 position switching valve 22, and these switching valves 20 to 22 are switched to 2 positions by an external pilot pressure, for example, air pressure. That is, as will be described later, when the retarder main body R is not in operation, no air pressure is supplied to any of the switching valves, and the switching valves 20 to 22 are in the first switching positions 20A to 22A shown in FIG. Retarder body R
Side and the oil passage 12 on the connector 12a side are both connected to an oil passage communicating with the oil reservoir 30, the oil passage 14 on the retarder main body R side is closed, and the oil passage 14 on the connector 14a side is an oil passage described later. It is connected to one end of 17. On the other hand, when the retarder body R is operated, air pressure is supplied to all the switching valves 20-22, and the switching valves 20-22 are switched to the second switching positions 20B-22B.
The discharge hole 2a and the suction hole 2b of the retarder body R are provided with oil passages 12, 13,
13 'and 14 are connected to form a hydraulic oil circulation oil passage.
前記管路13及び13′の各他端にはオイルクーラ32が接続
され、オイルクーラ32とコネクタ12a間の管路13の分岐
点13aには管路18の一端が接続され、管路18の他端には
リザーバ34が接続されている。実際にはリザーバ34はオ
イルクーラ32に一体に組み込まれており、両者はクーラ
ヘッドにより接続されている。そして、オイルクーラ32
は、第２図に示すようにエンジンＥの下方、且つ、ラジ
エータ36近傍に配設される。ラジエータ36で冷却された
冷却水はパイプ39を介してオイルクーラ32に供給され、
オイルクーラ32を通る作動油を冷却した後、冷却水循環
ポンプ38を介してエンジンＥに供給されエンジンＥを冷
却してラジエータ36に戻される。一方、リザーバ34は、
シリンダ34a内を摺動し、空気圧作動のピストン34bを有
し、このピストン34bをシリンダ34aから引き出すことに
よって、リターダ本体Ｒの非作動時にリターダ本体Ｒか
ら排出される作動油を貯えると共に、この貯えた作動油
をリターダ本体Ｒの作動時にピストン34bにより一気に
リターダ本体Ｒに向けて押し出すことによりリターダ本
体Ｒによる吸収馬力の発生、即ち、応答性を早めるよう
にしている。An oil cooler 32 is connected to each of the other ends of the pipelines 13 and 13 ', and one end of a pipeline 18 is connected to a branch point 13a of the pipeline 13 between the oil cooler 32 and the connector 12a. A reservoir 34 is connected to the other end. Actually, the reservoir 34 is integrally incorporated in the oil cooler 32, and both are connected by a cooler head. And the oil cooler 32
Is disposed below the engine E and near the radiator 36 as shown in FIG. The cooling water cooled by the radiator 36 is supplied to the oil cooler 32 via the pipe 39,
After the hydraulic oil passing through the oil cooler 32 is cooled, it is supplied to the engine E via the cooling water circulation pump 38 to cool the engine E and then returned to the radiator 36. On the other hand, the reservoir 34
It has a pneumatically operated piston 34b that slides in the cylinder 34a. By pulling out this piston 34b from the cylinder 34a, the hydraulic oil discharged from the retarder main body R when the retarder main body R is not in operation is stored, and this storage oil is also stored. When the retarder main body R is operated, the hydraulic oil is pushed out toward the retarder main body R at once by the piston 34b, so that absorption horsepower is generated by the retarder main body R, that is, responsiveness is accelerated.
前記油路17の他端側は３ポート２位置切換弁24のポート
24aに接続され、油路17の途中には第１の調圧制御弁26
が配設される。切換弁24のポート24cには油路15の一端
が接続され、油路15の他端はオイル溜30に連通してお
り、油路15途中にはオイルポンプ４が配設されている。
前記吸入孔2bと切換弁22間の油路14の分岐点14bには油
路16の一端が接続され、油路16の他端は切換弁24のポー
ト24bに接続され、該油路16途中には第２の調圧制御弁2
8が配設されている。調圧制御弁26及び28はいずれも内
部パイロット方式リリーフ付の調圧弁であり、第１の調
圧制御弁26は、その下流圧がフィードバックされて調圧
制御弁26の図示しないスプールの一端面に作用し、該ス
プールの他端面を押圧するバネ26aのバネ力と釣り合う
位置にスプールを移動させ、調圧制御弁26から吐出され
る作動油の吐出圧を低圧側の所定圧（例えば、１〜2kg/
cm2）に調圧する。そして、後述するオイルポンプ４か
ら調圧制御弁26に供給される余剰の作動油は調圧制御弁
26に接続される油路17aを介してオイル溜30に戻され
る。一方、第２の調圧制御弁28もその下流圧がフィード
バックされて調圧制御弁28の図示しないスプールの一端
面に作用し、該スプールの他端面を押圧するバネ28aの
バネ力と釣り合う位置にスプールを移動させ、調圧制御
弁28から吐出される作動油の吐出圧を前記第１の調圧制
御弁26の所定吐出圧より高い所定圧（例えば、４〜5kg/
cm2）に調圧する。そして、オイルポンプ４から調圧制
御弁28に供給される余剰の作動油は調圧制御弁28に接続
される油路16aを介してオイル溜30に戻される。The other end of the oil passage 17 is a port of the 3-port 2-position switching valve 24.
The first pressure adjusting control valve 26 connected to the oil passage 17 is provided in the middle of the oil passage 17.
Is provided. One end of the oil passage 15 is connected to the port 24c of the switching valve 24, the other end of the oil passage 15 communicates with the oil sump 30, and an oil pump 4 is arranged in the middle of the oil passage 15.
One end of the oil passage 16 is connected to the branch point 14b of the oil passage 14 between the suction hole 2b and the switching valve 22, and the other end of the oil passage 16 is connected to the port 24b of the switching valve 24. The second pressure regulation control valve 2
8 are arranged. The pressure regulating control valves 26 and 28 are both pressure regulating valves with an internal pilot type relief, and the first pressure regulating control valve 26 is fed back with its downstream pressure and one end face of the spool (not shown) of the pressure regulating control valve 26 is fed back. And moves the spool to a position that balances the spring force of the spring 26a that presses the other end surface of the spool, and the discharge pressure of the hydraulic oil discharged from the pressure control valve 26 is reduced to a predetermined pressure on the low pressure side (for example, 1 ~ 2kg /
Adjust the pressure to cm 2 ). The excess hydraulic oil supplied from the oil pump 4 described later to the pressure control valve 26 is the pressure control valve.
It is returned to the oil sump 30 via an oil passage 17 a connected to 26. On the other hand, the downstream pressure of the second pressure control valve 28 is also fed back and acts on one end surface of the spool (not shown) of the pressure control valve 28 to balance the spring force of the spring 28a that presses the other end surface of the spool. The spool is moved to a predetermined pressure so that the discharge pressure of the hydraulic oil discharged from the pressure control valve 28 is higher than the predetermined discharge pressure of the first pressure control valve 26 (for example, 4 to 5 kg /
Adjust the pressure to cm 2 ). Then, excess hydraulic oil supplied from the oil pump 4 to the pressure control valve 28 is returned to the oil reservoir 30 via the oil passage 16a connected to the pressure control valve 28.
前記切換弁24は外部のパイロット圧（空気圧）により２
位置に切り換えられ、後述するようにリターダ本体Ｒの
非作動時には空気圧が切換弁24に供給されず、切換弁24
は第１図に示す第１の切換位置24Aの状態にあり、油路1
5が油路17に接続され、オイルポンプ４から吐出される
作動油が第１の調圧制御弁26に供給される。一方、リタ
ーダ本体Ｒの作動時には空気圧が切換弁24に供給され、
切換弁24は第２の切換位置24Bに切り換えられ、油路15
は通路16に切り換え接続され、オイルポンプ４から吐出
される作動油が第２の調圧制御弁28に供給される。The switching valve 24 is set to 2 by the external pilot pressure (air pressure).
When the retarder main body R is not operated, the air pressure is not supplied to the switching valve 24 as described below.
Is in the state of the first switching position 24A shown in FIG.
5 is connected to the oil passage 17, and the hydraulic oil discharged from the oil pump 4 is supplied to the first pressure control valve 26. On the other hand, when the retarder body R is operated, air pressure is supplied to the switching valve 24,
The switching valve 24 is switched to the second switching position 24B, and the oil passage 15
Is switched and connected to the passage 16, and the hydraulic oil discharged from the oil pump 4 is supplied to the second pressure control valve 28.
次に、油圧リターダ装置の作用を説明する。Next, the operation of the hydraulic retarder device will be described.
先ず、リターダ本体Ｒの非作動時には総ての切換弁20〜
22,24には空気圧が供給されず、第１図に示す第１の切
換位置に切り換えられている。従って、リターダ本体Ｒ
内の作動油の大部分はリザーバ34に貯えられると共に残
部がオイル溜30に排出され、この状態ではリターダ本体
Ｒはクランク軸10の回転馬力を吸収する作用がなく、エ
ンジンＥに対して何らの影響を与えない。First, when the retarder body R is not in operation, all the switching valves 20 to
No air pressure is supplied to 22, 24 and they are switched to the first switching position shown in FIG. Therefore, the retarder body R
Most of the hydraulic oil therein is stored in the reservoir 34 and the rest is discharged to the oil reservoir 30. In this state, the retarder main body R has no function of absorbing the rotational horsepower of the crankshaft 10, and has no effect on the engine E. It has no effect.
一方、オイル溜30から吸い上げられ、オイルポンプ４か
ら送出される作動油は切換弁24→第１の調圧制御弁26→
切換弁22→オイルクーラ32→切換弁21→オイル溜30の経
路で循環し、作動油がオイルクーラ32を通過する際に、
冷却水循環ポンプ38により供給される冷却水と熱交換さ
れて冷却される。このとき、第１の調圧制御弁26は前述
の通りオイルポンプ４の吐出圧を低圧（１〜2kg/cm2）
に保つのでオイルポンプ４の負荷が小さく、オイルポン
プ４を駆動するに必要な馬力が小さくて済む。On the other hand, the hydraulic oil sucked up from the oil sump 30 and delivered from the oil pump 4 is changed over by the switching valve 24 → the first pressure control valve 26 →
When the working oil circulates in the path of the switching valve 22 → the oil cooler 32 → the switching valve 21 → the oil sump 30 and the working oil passes through the oil cooler 32,
It is cooled by exchanging heat with the cooling water supplied by the cooling water circulation pump 38. At this time, the first pressure control valve 26 reduces the discharge pressure of the oil pump 4 to a low pressure (1-2 kg / cm 2 ) as described above.
Therefore, the load on the oil pump 4 is small and the horsepower required to drive the oil pump 4 is small.
次に、車両運転席近傍に設けてある図示しないリターダ
スイッチをオンにすると図示しない電磁弁が切り換えら
れ、エアタンク（図示せず）に貯えられている空気圧が
切換弁20〜22,24及びリザーバ34に供給され、切換弁20
〜21,24が第２の切換位置に切り換えられると同時にリ
ザーバ34のピストン34bがリザーバ34に貯えられている
作動油をリターダ本体Ｒに向かって押し出す。このと
き、リザーバ34がオイルクーラ32の近傍に配設されてい
るので、リザーバ34から押し出される作動油は分岐点13
aから作動油循環油路を右回り及び左回りに略等距離の
油路を介してリターダ本体Ｒに供給されることになり、
リターダ本体Ｒ及び油路12,14等に充填される作動油の
充填時間を短くすることが出来る。リターダ本体Ｒはそ
のロータ３がステータ２に対して相対回転することによ
り運動エネルギが熱エネルギとして作動油に吸収され、
高温になった作動油が排出孔2aから吐き出される。吐き
出された作動油は作動油循環油路である油路12〜14を循
環し、オイルクーラ32で冷却されて吸入孔2bから再びリ
ターダ本体Ｒに供給される。Next, when a retarder switch (not shown) provided in the vicinity of the driver's seat of the vehicle is turned on, a solenoid valve (not shown) is switched, and the air pressure stored in the air tank (not shown) is changed over by the switching valves 20 to 22, 24 and the reservoir 34. Is supplied to the switching valve 20
21 to 24 are switched to the second switching position, and at the same time, the piston 34b of the reservoir 34 pushes the hydraulic oil stored in the reservoir 34 toward the retarder body R. At this time, since the reservoir 34 is arranged in the vicinity of the oil cooler 32, the hydraulic oil pushed out from the reservoir 34 will not reach the branch point 13.
It will be supplied to the retarder main body R from the hydraulic oil circulating oil passage from a through clockwise and counterclockwise oil passages at substantially equal distances.
It is possible to shorten the filling time of the hydraulic oil that is filled in the retarder main body R, the oil passages 12, 14, and the like. When the rotor 3 of the retarder body R rotates relative to the stator 2, the kinetic energy is absorbed by the working oil as heat energy,
The hydraulic oil having a high temperature is discharged from the discharge hole 2a. The discharged working oil circulates through the oil passages 12 to 14 which are working oil circulation oil passages, is cooled by the oil cooler 32, and is supplied to the retarder body R again from the suction hole 2b.
一方、オイルポンプ４から吐出される作動油は第２の切
換位置に切り換えられた切換弁24を介して第２の調圧制
御弁28に供給され、この第２の調圧制御弁28により前記
第１の調圧制御弁26で調圧されるより高い所定圧（４〜
5kg/cm2）に調圧されて作動油循環油路である油路14に
押し込まれる。即ち、作動油循環油路を循環する作動油
量オイル溜30側に漏れ出て油路内の圧力が低下すると、
圧力の低下を補うようにオイル溜30→オイルポンプ４→
切換弁24→調圧制御弁28→油路14の経路で作動油が補給
され、作動油循環油路は常に前記所定圧（４〜5kg/c
m2）に保持される。このとき、オイルポンプ４から吐出
される作動油の大部分はリリーフされて油路16aを介し
てオイル溜30に戻されるが、調圧制御弁28の設定圧が第
１の調圧制御弁26より高く設定されているのでオイルポ
ンプ４の負荷は作動油が第１の調圧制御弁26で調圧され
るよりも高くなる。On the other hand, the hydraulic oil discharged from the oil pump 4 is supplied to the second pressure control valve 28 via the switching valve 24 switched to the second switching position. A higher predetermined pressure (4 to 4) regulated by the first pressure regulation control valve 26.
The pressure is adjusted to 5 kg / cm 2 ) and the oil is pushed into the oil passage 14 which is a hydraulic oil circulation oil passage. That is, when the amount of hydraulic oil circulating in the hydraulic oil circulation oil passage leaks to the oil reservoir 30 side and the pressure in the oil passage decreases,
Oil sump 30 → oil pump 4 → to compensate for pressure drop
The hydraulic oil is replenished through the path of the switching valve 24 → the pressure regulation control valve 28 → the oil passage 14, and the hydraulic oil circulating oil passage always keeps the predetermined pressure (4 to 5 kg / c
m 2 ). At this time, most of the hydraulic oil discharged from the oil pump 4 is relieved and returned to the oil reservoir 30 via the oil passage 16a, but the set pressure of the pressure control valve 28 is the first pressure control valve 26. Since the oil pump 4 is set higher, the load on the oil pump 4 becomes higher than that of the hydraulic oil regulated by the first pressure control valve 26.
第３図は本考案の第２の実施例を示し、同図中第１図と
同じ符号を付したものは第１図に示すものと実質的に同
じであるので、それらの詳細な説明を省略する。FIG. 3 shows a second embodiment of the present invention, in which the same reference numerals as those in FIG. 1 are substantially the same as those shown in FIG. Omit it.
第２の実施例では油路14に配設されていた第１図の切換
弁22に代えて遮断弁40が配設される。この遮断弁40は空
気圧で２位置に切り換えられ、空気圧が供給されないと
きには第３図に示す第１の切換位置40Aに切り換えられ
て油路14を遮断し、空気圧が供給されるときには第２の
切換位置40Bに切り換えられ、油路40を開成させる。
又、油路14の分岐点14bには油路16が接続されていた
が、第２の実施例ではこれに代えて、遮断弁40とコネク
タ14a間の油路14の分岐点14cに油路42の一端が接続さ
れ、油路42の他端はオイルポンプ４に接続される。そし
て、油路42の途中には調圧制御弁44が配設されている。In the second embodiment, a cutoff valve 40 is provided instead of the switching valve 22 shown in FIG. This shut-off valve 40 is switched to the 2 position by air pressure, and when the air pressure is not supplied, it is switched to the first switch position 40A shown in FIG. 3 to shut off the oil passage 14, and when the air pressure is supplied, the second switch position 40A is shut off. The position is switched to the position 40B to open the oil passage 40.
Further, the oil passage 16 is connected to the branch point 14b of the oil passage 14, but instead of this, in the second embodiment, the oil passage 16 is connected to the branch point 14c of the oil passage 14 between the shutoff valve 40 and the connector 14a. One end of 42 is connected, and the other end of the oil passage 42 is connected to the oil pump 4. A pressure adjustment control valve 44 is arranged in the oil passage 42.
調圧制御弁44は、一端部に大径端面と小径端面を有し、
他端面をバネ44aが押圧する、図示しないスプールを備
えており、前記大径端面にはパイロット油路44bを介し
て、前記小径端面にはパイロット油路44cを介して夫々
調圧制御弁44の下流圧が導かれ、大径端面に使用する圧
力と小径端面に作用する圧力の合力が前記バネ44aのバ
ネ力と釣り合う位置にスプールを移動させて、オイルポ
ンプ４から吐出される作動油の吐出圧を所定値に調圧す
る。そして、前記パイロット油路44c途中には３ポート
２位置切換弁46が配設されている。この切換弁46も空気
圧により２位置に切り換えられるものであり、空気圧が
供給されない場合には第３図に示す第１の切換位置46A
に切り換えられてパイロット油路44cは遮断され、前記
小径端面はオイル溜30に連通する。一方、空気圧が切換
弁46に供給される場合には第２の切換位置46Bに切り換
えられ、パイロット油路44cは開成されて調圧制御弁44
の下流圧がパイロット油路44cを介して前記小径端面に
導かれることになる。The pressure control valve 44 has a large diameter end surface and a small diameter end surface at one end,
A spool (not shown), which is pressed by the spring 44a to the other end surface, is provided. The pilot oil passage 44b is provided on the large-diameter end surface, and the pilot oil passage 44c is provided on the small-diameter end surface. The downstream pressure is introduced, the spool is moved to a position where the resultant force of the pressure used on the large diameter end surface and the pressure acting on the small diameter end surface balances the spring force of the spring 44a, and the hydraulic oil discharged from the oil pump 4 is discharged. Adjust the pressure to a specified value. A 3-port / 2-position switching valve 46 is arranged in the pilot oil passage 44c. This switching valve 46 is also switched to two positions by air pressure, and when air pressure is not supplied, the first switching position 46A shown in FIG. 3 is used.
The pilot oil passage 44c is cut off and the small diameter end face communicates with the oil reservoir 30. On the other hand, when air pressure is supplied to the switching valve 46, it is switched to the second switching position 46B, the pilot oil passage 44c is opened, and the pressure control valve 44 is opened.
Will be guided to the small-diameter end surface via the pilot oil passage 44c.
リターダ本体Ｒが非作動時には、総ての切換弁20,21,40
及び46に空気圧が供給されず、第３図に示す第１の切換
位置に切り換えられており、切換弁46によりパイロット
油路44cが遮断されるため、調圧制御弁44の前記スプー
ルの小径端面には下流圧が作用しない。従って、調圧制
御弁44のスプールは大径端面に作用する圧力と他端面に
作用するバネ44aのバネ力が釣り合う位置に移動してオ
イルポンプ４から吐出される作動油の吐出圧を低圧側の
所定圧（１〜2kg/cm2）に調圧し、この作動油をオイル
クーラ32→切換弁21→オイル溜30の経路を介して循環さ
せる。When the retarder body R is inactive, all switching valves 20, 21, 40
And 46 are not supplied with air pressure and are switched to the first switching position shown in FIG. 3, and the switching valve 46 shuts off the pilot oil passage 44c, so that the small-diameter end surface of the spool of the pressure control valve 44 is closed. Downstream pressure does not act on. Therefore, the spool of the pressure control valve 44 moves to a position where the pressure acting on the large-diameter end surface and the spring force of the spring 44a acting on the other end surface are balanced and the discharge pressure of the hydraulic oil discharged from the oil pump 4 is reduced to the low pressure side. Is adjusted to a predetermined pressure (1 to 2 kg / cm 2 ) and the operating oil is circulated through the path of the oil cooler 32 → the switching valve 21 → the oil reservoir 30.
一方、リターダ本体Ｒの作動時には総ての切換弁20,21,
40及び46に空気圧が供給されて夫々第２の切換位置に切
り換えられ、パイロット油路44cが開成される。このた
め、調圧制御弁44の前記スプールの小径端面には下流圧
が作用するため、スプールはこの小径端面に作用する圧
力及び前記大径端面に作用する圧力の合力と前記バネ44
aのバネ力とが釣り合う位置に移動してオイルポンプ４
から吐出される作動油の吐出圧を高圧側の所定圧（４〜
5kg/cm2）に調圧し、この作動油を作動油循環油路であ
る油路14に押し込み補給する。On the other hand, when the retarder body R is operated, all the switching valves 20, 21,
Air pressure is supplied to 40 and 46 to switch to the second switching position respectively, and the pilot oil passage 44c is opened. Therefore, the downstream pressure acts on the small-diameter end surface of the spool of the pressure control valve 44, and the spool therefore exerts a combined force of the pressure acting on the small-diameter end surface and the pressure acting on the large-diameter end surface and the spring 44.
Move to a position where the spring force of a balances with the oil pump 4
The discharge pressure of the hydraulic oil discharged from the
The pressure is adjusted to 5 kg / cm 2 ) and this hydraulic oil is pushed into the oil passage 14 which is the hydraulic oil circulation oil passage to replenish it.
斯くして、調圧制御弁44はリターダ本体Ｒの非作動時に
は作動油圧を低圧側の所定圧に、作動時には高圧側の所
定圧に夫々調圧し、第１図に示す２個の調圧制御弁26及
び28と同等の機能を発揮することになる。Thus, the pressure regulation control valve 44 regulates the working oil pressure to a predetermined pressure on the low pressure side when the retarder body R is not operated, and to a predetermined pressure on the high pressure side when the retarder main body R is not operated. It will perform the same function as valves 26 and 28.
上述の実施例では本考案の油圧リターダ装置のリターダ
本体を内燃エンジンのクランク軸に取り付けた場合を例
に説明したが、本考案はこれに限定されずエンジンの出
力軸から車輪に至る駆動力伝達経路途中であればリター
ダ本体をどこに取り付けてもよい。In the above-described embodiment, the case where the retarder body of the hydraulic retarder device of the present invention is attached to the crankshaft of the internal combustion engine has been described as an example, but the present invention is not limited to this, and the driving force transmission from the output shaft of the engine to the wheels is transmitted. The retarder body may be attached anywhere along the route.
又、上述の２つの実施例は本考案の油圧リターダ装置を
車両のリターダ装置に適用したものであるが、本考案は
これに限定されず種々の分野のリターダ装置として使用
することができ、例えば、本考案の油圧リターダ装置を
クレーン装置のワイヤ巻取胴に取り付け、油圧リターダ
装置を作動させて吊り下げた重量物を徐々に卸していく
場合に有効である。Further, although the above-mentioned two embodiments apply the hydraulic retarder device of the present invention to the retarder device of a vehicle, the present invention is not limited to this and can be used as retarder devices of various fields. The present invention is effective when the hydraulic retarder device of the present invention is attached to the wire winding cylinder of the crane device and the hydraulic retarder device is operated to gradually unload the suspended heavy object.
（考案の効果） 以上詳述したように本考案の油圧リターダ装置に依れ
ば、オイルポンプと作動油循環油路間にオイルポンプが
吐出する作動油の吐出圧を高低２段に切り換える油圧調
整切換手段を配設すると共に、作動油循環油路途中に、
リターダ本体の作動時に作動油を作動油循環油路を循環
させ、非作動時にリターダ本体内の作動油をオイル溜に
排出させると共に、オイルポンプから吐出される作動油
をオイルクーラを介してオイル溜に排出させる油路切換
手段を配設し、油圧調整切換手段はリターダ本体の作動
時に作動油の吐出圧を高圧側に切り換え、非作動時に低
圧側に切り換えるように構成したので、リターダ本体の
非作動時にオイルポンプに不必要な負荷が掛からず、従
ってオイルポンプを駆動するのに必要な馬力に節約する
ことが出来、又、必要なときにだけオイルポンプから高
圧の作動油を吐出させるために、オイルポンプの寿命が
延びるという優れた効果を奏する。(Effects of the Invention) As described in detail above, according to the hydraulic retarder device of the present invention, the hydraulic pressure adjustment that switches the discharge pressure of the hydraulic oil discharged from the oil pump between the oil pump and the hydraulic oil circulation oil passage to two stages, high and low. A switching means is provided, and in the middle of the hydraulic oil circulation oil passage,
When operating the retarder main body, circulate the hydraulic oil in the hydraulic oil circulation oil passage, and when not operating, drain the hydraulic oil in the retarder main body to the oil sump, and at the same time store the hydraulic oil discharged from the oil pump through the oil cooler. The oil pressure switching means for discharging the hydraulic oil is arranged to switch the discharge pressure of the hydraulic oil to the high pressure side when the retarder body is operating and to the low pressure side when the retarder body is not operating. In operation, the oil pump is not unnecessarily loaded, therefore the horsepower required to drive the oil pump can be saved, and in order to discharge high pressure hydraulic oil from the oil pump only when necessary. The excellent effect of extending the life of the oil pump is achieved.
第１図は本考案の第１の実施例を示し、油圧リターダ装
置の油圧回路図、第２図は本考案の油圧リターダ装置の
取り付け状態を示す内燃エンジンの側面図、第３図は本
考案の第２の実施例を示し、第１図と類似の油圧リター
ダ装置の油圧回路図、第４図は油圧リターダ装置のリタ
ーダ本体の構成を示す断面図である。 ２…ステータ、３…ロータ、４…オイルポンプ、12…油
路、13,13′…管路、14…油路、20〜22…切換弁（油路
切換手段）、24…切換弁（油圧切換制御手段）、26,28
…調圧制御弁（油圧切換制御手段）、30…オイル溜、32
…オイルクーラ、34…リザーバ、40…遮断弁（油路切換
手段）、44…調圧制御弁（油圧切換制御手段）、46…切
換弁（油圧切換制御手段）、Ｒ…リターダ本体。FIG. 1 shows a first embodiment of the present invention, a hydraulic circuit diagram of a hydraulic retarder device, FIG. 2 is a side view of an internal combustion engine showing a mounted state of the hydraulic retarder device of the present invention, and FIG. 3 is a present invention. FIG. 4 is a hydraulic circuit diagram of a hydraulic retarder device similar to FIG. 1, and FIG. 4 is a cross-sectional view showing the structure of the retarder body of the hydraulic retarder device. 2 ... Stator, 3 ... Rotor, 4 ... Oil pump, 12 ... Oil passage, 13, 13 '... Pipe passage, 14 ... Oil passage, 20-22 ... Switching valve (oil passage switching means), 24 ... Switching valve (hydraulic pressure) Switching control means), 26, 28
… Pressure adjustment control valve (hydraulic pressure switching control means), 30… Oil sump, 32
... oil cooler, 34 ... reservoir, 40 ... shutoff valve (oil passage switching means), 44 ... pressure regulation control valve (hydraulic pressure switching control means), 46 ... switching valve (hydraulic pressure switching control means), R ... retarder main body.
Claims (1)
転させることにより作動油に運動エネルギが放熱されて
吸収馬力を得るリターダ本体（Ｒ）と、該リターダ本体
（Ｒ）に接続された作動油循環油路（12,13,13′,14）
途中に配設され、作動油を冷却するオイルクーラ（32）
と、前記作動油循環油路に作動油を補給するオイルポン
プ（４）とを備える油圧リターダ装置において、前記オ
イルポンプ（４）と前記作動油循環油路間に該オイルポ
ンプが吐出する作動油の吐出圧を高低２段に切り換える
油圧調整切換手段（24,26,28）（44,46）を配設すると
共に、前記作動油循環油路途中に、前記リターダ本体の
作動時に作動油を前記作動油循環油路を循環させ、非作
動時に前記リターダ本体内の作動油をオイル溜に排出さ
せると共に、前記オイルポンプから吐出される作動油を
前記オイルクーラを介して前記オイル溜に排出させる油
路切換手段（20,21,22）（20,21,40）を配設し、前記油
圧調整切換手段（24,26,28）（44,46）は前記リターダ
本体（Ｒ）の作動時に作動油の吐出圧を高圧側に切り換
え、非作動時に低圧側に切り換えることを特徴とする油
圧リターダ装置。1. A retarder main body (R) which obtains absorption horsepower by radiating kinetic energy to hydraulic oil by rotating a rotor (3) with respect to a stator (2), and is connected to the retarder main body (R). Hydraulic oil circulating oil passage (12,13,13 ', 14)
An oil cooler (32) installed midway to cool the hydraulic oil
And a hydraulic retarder device including an oil pump (4) for replenishing hydraulic oil to the hydraulic oil circulation oil passage, wherein the hydraulic oil discharged by the oil pump is between the oil pump (4) and the hydraulic oil circulation oil passage. Is provided with a hydraulic pressure adjustment switching means (24, 26, 28) (44, 46) for switching the discharge pressure of the hydraulic oil between high and low stages, and the hydraulic oil is provided in the middle of the hydraulic oil circulation passage when the retarder main body is operated. Oil that circulates through the hydraulic oil circulation passage and discharges the hydraulic oil in the retarder body to the oil sump when not operating, and discharges the hydraulic oil discharged from the oil pump to the oil sump via the oil cooler. Road switching means (20,21,22) (20,21,40) are provided, and the hydraulic pressure adjustment switching means (24,26,28) (44,46) are activated when the retarder body (R) is activated. Switching the oil discharge pressure to the high pressure side and to the low pressure side when not operating Hydraulic retarder and wherein the door.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10997387U JPH0635844Y2 (en) | 1987-07-20 | 1987-07-20 | Hydraulic retarder device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10997387U JPH0635844Y2 (en) | 1987-07-20 | 1987-07-20 | Hydraulic retarder device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6414559U JPS6414559U (en) | 1989-01-25 |
| JPH0635844Y2 true JPH0635844Y2 (en) | 1994-09-21 |
Family
ID=31346707
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10997387U Expired - Lifetime JPH0635844Y2 (en) | 1987-07-20 | 1987-07-20 | Hydraulic retarder device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0635844Y2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20230075045A (en) * | 2021-11-22 | 2023-05-31 | 현대트랜시스 주식회사 | Control apparatus for retarder |
| KR20230082399A (en) * | 2021-12-01 | 2023-06-08 | 현대트랜시스 주식회사 | Control apparatus for retarder |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104029664B (en) * | 2014-06-20 | 2016-05-11 | 吉林大学 | A kind of Retarder of the windage loss eliminated with blocking device and oil circuit control |
-
1987
- 1987-07-20 JP JP10997387U patent/JPH0635844Y2/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20230075045A (en) * | 2021-11-22 | 2023-05-31 | 현대트랜시스 주식회사 | Control apparatus for retarder |
| KR20230082399A (en) * | 2021-12-01 | 2023-06-08 | 현대트랜시스 주식회사 | Control apparatus for retarder |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6414559U (en) | 1989-01-25 |
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