JPH0527423U - Transmission hydraulic circuit with priority to clutch operation - Google Patents
Transmission hydraulic circuit with priority to clutch operationInfo
- Publication number
- JPH0527423U JPH0527423U JP8249891U JP8249891U JPH0527423U JP H0527423 U JPH0527423 U JP H0527423U JP 8249891 U JP8249891 U JP 8249891U JP 8249891 U JP8249891 U JP 8249891U JP H0527423 U JPH0527423 U JP H0527423U
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- circuit
- lubrication
- transmission
- pressure pump
- 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.)
- Pending
Links
Landscapes
- General Details Of Gearings (AREA)
- Gear-Shifting Mechanisms (AREA)
- Control Of Transmission Device (AREA)
Abstract
(57)【要約】
【目的】 トランスミッションのクラッチ作動油量と潤
滑油量の配分を適正化し、ト−タルのポンプ吐出におけ
る駆動馬力を最小限にすることを目的としたもの。
【構成】 クラッチ作動用の小容量高圧ポンプ１をクラ
ッチ回路２に接続し、潤滑用の大容量低圧ポンプ３を潤
滑回路４に接続した変速機の油圧回路において、潤滑回
路４にクラッチ作動時、クラッチ回路２の油圧により切
り換えられて大容量低圧ポンプ３の吐出油をクラッチ回
路２に供給する優先バルブ５を設けると共に、クラッチ
回路２と潤滑回路３とをクラッチ作動用のリリ−フバル
ブ６を介して接続したもの。
【効果】 クラッチ作動油量と潤滑油量の配分が適切と
なりポンプの必要駆動馬力は約１／３に低減でき、有効
馬力伝達を増加できる。
(57) [Summary] [Purpose] The objective is to optimize the distribution of clutch operating oil and lubricating oil in the transmission to minimize the driving horsepower in the total pump discharge. [Structure] In a hydraulic circuit of a transmission in which a small capacity high pressure pump 1 for clutch operation is connected to a clutch circuit 2 and a large capacity low pressure pump 3 for lubrication is connected to a lubrication circuit 4, when a clutch is operated in the lubrication circuit 4, A priority valve 5 for switching the hydraulic pressure of the clutch circuit 2 to supply the discharge oil of the large-capacity low-pressure pump 3 to the clutch circuit 2 is provided, and the clutch circuit 2 and the lubrication circuit 3 are connected via a relief valve 6 for clutch operation. Connected. [Effect] The distribution of the amount of clutch operating oil and the amount of lubricating oil becomes appropriate, the required driving horsepower of the pump can be reduced to about 1/3, and the effective horsepower transmission can be increased.
Description
【０００１】[0001]
本考案は変速機のクラッチ回路および潤滑回路における制御に係り、特にクラ ッチ作動優先の変速機油圧回路に関する。 The present invention relates to control in a clutch circuit and a lubrication circuit of a transmission, and more particularly to a transmission hydraulic circuit in which clutch operation has priority.
【０００２】[0002]
従来から変速段の切換えを油圧クラッチのＯＮ，ＯＦＦにより行う変速機にお いては、図２に示すように同一の油圧ポンプ２１の吐出量をトルクコンバ−タ２ ２の作動や図示しない変速機のクラッチ２３作動用と、変速機の潤滑用とに使用 している。そして油圧としては、例えば作動用は３８kg／cm2 、潤滑用は２．７ kg／cm2 が用いられている。図中、２４は変速機潤滑室、２５はリリ−フバルブ 、２６は変速機潤滑バルブ、２７，２８はそれぞれオイルフィルタである。2. Description of the Related Art Conventionally, in a transmission in which a gear shift is performed by turning on and off a hydraulic clutch, as shown in FIG. 2, the same hydraulic pump 21 discharges the same amount of discharge as the torque converter 22 and a transmission (not shown). It is used to operate the clutch 23 and to lubricate the transmission. As the hydraulic pressure, for example, 38 kg / cm 2 for operation and 2.7 kg / cm 2 for lubrication are used. In the figure, 24 is a transmission lubrication chamber, 25 is a relief valve, 26 is a transmission lubrication valve, and 27 and 28 are oil filters.
【０００３】[0003]
ところで油圧ポンプ２１の吐出量はトルクコンバ−タ２２や変速機の作動用と 、変速機の潤滑用のそれぞれの必要量の多い方で決定されている。そして通常は 変速機の潤滑用が多いため、その量に見合ったポンプの大きさが選定されている 。すなわち、低油圧側の油量を基準として変速機の作動用は高圧制御することに なる。したがってポンプ２１の吐出側のリリ−フバルブ２５のセット圧は高圧と なり常に全油量を高油圧で使用しなければならないことから、ポンプ２１は駆動 馬力の大きなものが必要となる。しかし潤滑用の場合は高圧を必要としないから 、 差し引いた高圧分の動力伝達馬力が損失となる問題があった。 By the way, the discharge amount of the hydraulic pump 21 is determined depending on which of the torque converter 22 and the transmission is required, and which is required for lubrication of the transmission. And, because the transmission is usually used for lubrication, the size of the pump is selected according to the amount. That is, the operation of the transmission is controlled at high pressure with reference to the oil amount on the low oil pressure side. Therefore, the set pressure of the relief valve 25 on the discharge side of the pump 21 becomes high, and the total amount of oil must be constantly used at high hydraulic pressure. Therefore, the pump 21 needs to have a large driving horsepower. However, in the case of lubrication, since high pressure is not required, there was a problem that the power transmission horsepower equivalent to the subtracted high pressure was lost.
【０００４】 本考案はこれに鑑み、変速機のクラッチ作動油量と潤滑油量の配分を適正化し 、ト−タルのポンプ吐出における駆動馬力を最小限にすることの出来るクラッチ 作動優先の変速機油圧回路を提供して従来技術の持つ欠点の解消を図ることを目 的としてなされたものである。In view of the above, the present invention optimizes the distribution of the clutch operating oil amount and the lubricating oil amount of the transmission, and can minimize the driving horsepower in the total pump discharge. The purpose was to provide a hydraulic circuit to overcome the drawbacks of the prior art.
【０００５】[0005]
上記従来技術の問題点を解決する手段として本考案は、クラッチ作動用の小容 量高圧ポンプをクラッチ回路に接続し、潤滑用の大容量低圧ポンプを潤滑回路に 接続した変速機の油圧回路において、該潤滑回路にクラッチ作動時、クラッチ回 路の油圧により切り換えられて大容量低圧ポンプの吐出油をクラッチ回路に供給 する優先バルブを設けると共に、前記クラッチ回路と潤滑回路とをクラッチ作動 用のリリ−フバルブを介して接続したことを特徴とする。 As a means for solving the above-mentioned problems of the prior art, the present invention provides a hydraulic circuit of a transmission in which a small capacity high pressure pump for clutch operation is connected to a clutch circuit and a large capacity low pressure pump for lubrication is connected to a lubrication circuit. When the clutch is activated, the lubrication circuit is provided with a priority valve that is switched by the hydraulic pressure of the clutch circuit to supply the discharge oil of the large-capacity low-pressure pump to the clutch circuit. -It is characterized in that it is connected via a valve.
【０００６】[0006]
上記構成によれば、クラッチ作動時にはクラッチフィル用として低圧用を優先 して作動に追加使用でき、潤滑の場合は高圧用と低圧用を合流させて内部リ−ク 等を除く全油量を潤滑用に使用することができる。 According to the above structure, when the clutch is operating, the low pressure can be preferentially additionally used as the clutch fill, and in the case of lubrication, the high pressure and the low pressure can be combined to lubricate the total amount of oil except the internal leak. Can be used for
【０００７】[0007]
図１は本考案にかかるクラッチ作動優先の変速機油圧回路の一実施例を示す。 FIG. 1 shows an embodiment of a transmission hydraulic circuit according to the present invention in which the clutch operation is prioritized.
【０００８】 本考案は、クラッチ作動用の小容量高圧ポンプ１をクラッチ回路２に接続し、 潤滑用の大容量低圧ポンプ３を潤滑回路４に接続した変速機の油圧回路において 、該潤滑回路４にクラッチ作動時、クラッチ回路２の油圧により切り換えられて 大容量低圧ポンプ３の吐出油をクラッチ回路２に供給する優先バルブ５を設ける と共に、前記クラッチ回路２と潤滑回路３とをクラッチ作動用のリリ−フバルブ ６を介して接続したものにより構成されている。The present invention relates to a hydraulic circuit of a transmission in which a small capacity high pressure pump 1 for clutch operation is connected to a clutch circuit 2 and a large capacity low pressure pump 3 for lubrication is connected to a lubrication circuit 4. The clutch valve 2 is provided with a priority valve 5 which is switched by the hydraulic pressure of the clutch circuit 2 to supply the discharge oil of the large-capacity low-pressure pump 3 to the clutch circuit 2, and the clutch circuit 2 and the lubricating circuit 3 are used for clutch operation. It is constituted by those connected via a relief valve 6.
【０００９】 前記小容量高圧ポンプ１と大容量低圧ポンプ３とは同一の駆動モ−タ７により 駆動され、小容量高圧ポンプ１の吐出側のクラッチ回路２は二又に分かれて一方 は、リリ−フバルブ６を介してトルクコンバ−タ８の図示しないバルブや変速機 潤滑バルブ９を経て変速機潤滑を行うように連結され、他方は変速機の変速のた めのクラッチ１０に連結されている。このクラッチ１０は各種（例えば、ハイク ラッチ、ロ−クラッチ、１速クラッチ、２速クラッチ等）あるが、ここでは代表 した１個で示す。また、大容量低圧ポンプ３の吐出側の潤滑回路４は前記リリ− フバルブ６に接続された回路と合流して潤滑入口に設けた前記変速機潤滑バルブ ９に接続されている。前記優先バルブ５は２位置ａ，ｂを有する切換えバルブで 潤滑回路４に設けられ、前記クラッチ回路２とは回路１１により連結され、回路 １１の他方は優先バルブ５のａ側に、また、回路１１から分岐したパイロット回 路１２は優先バルブ５を切り換える側に接続されている。そして優先バルブ５の 一側にはばね１３が設けられ、これにより変速状態でない時は、クラッチ回路２ が昇圧されており、優先バルブ５は通常ｂ位置にセットされている。図中、１４ ，１５はオイルフィルタ、１６は変速機潤滑室、１７はタンクである。ここで小 容量高圧ポンプ１は変速機回路の内部リ−ク油量分を補充できる吐出量を有して リリ−フバルブ６のセット圧は、この実施例でば３８kg／cm2 としており、大容 量低圧ポンプ３は変速機潤滑油量により吐出量が設定され、潤滑バルブ９のクラ ッキング圧は２．７kg／cm2 となっている。The small-capacity high-pressure pump 1 and the large-capacity low-pressure pump 3 are driven by the same drive motor 7, and the discharge side clutch circuit 2 of the small-capacity high-pressure pump 1 is bifurcated and one is A valve (not shown) of a torque converter 8 and a gearbox lubrication valve 9 are connected via a valve 6 to perform gearbox lubrication, and the other is connected to a clutch 10 for gearshifting the gearbox. There are various types of the clutch 10 (for example, a high clutch, a low clutch, a first speed clutch, a second speed clutch, etc.), but here, only one representative one is shown. The lubrication circuit 4 on the discharge side of the large-capacity low-pressure pump 3 joins the circuit connected to the relief valve 6 and is connected to the transmission lubrication valve 9 provided at the lubrication inlet. The priority valve 5 is a switching valve having two positions a and b and is provided in the lubrication circuit 4 and is connected to the clutch circuit 2 by a circuit 11. The other of the circuits 11 is on the a side of the priority valve 5 and the circuit. The pilot circuit 12 branched from 11 is connected to the side for switching the priority valve 5. A spring 13 is provided on one side of the priority valve 5, whereby the clutch circuit 2 is boosted when not in the gear shift state, and the priority valve 5 is normally set to the b position. In the figure, 14 and 15 are oil filters, 16 is a transmission lubricating chamber, and 17 is a tank. Here, the small-capacity high-pressure pump 1 has a discharge amount capable of supplementing the internal leak oil amount of the transmission circuit, and the set pressure of the relief valve 6 is 38 kg / cm 2 in this embodiment. The discharge amount of the capacity low-pressure pump 3 is set by the amount of transmission lubricating oil, and the cracking pressure of the lubricating valve 9 is 2.7 kg / cm 2 .
【００１０】 つぎに作用を説明する。駆動モ−タ７により駆動された小容量高圧ポンプ１と 大容量低圧ポンプ３の吐出油（低圧）はそれぞれクラッチ回路２および潤滑回路 ４を経て変速機潤滑バルブ９から変速機潤滑に使用されるが、この状態のとき優 先バルブ５はばね１３によりａ位置にあり、したがって大容量低圧ポンプ３の吐 出油は優先バルブ５を通過した吐出油が潤滑回路４の下流に流れて変速機が潤滑 される。つぎに変速機を前後進あるいは変速のために切換えるクラッチ作動時に は、小容量高圧ポンプ１からの吐出油（高圧）はクラッチ１０に流れ、クラッチ ピストンを満たすまでは油圧は低下し、同時に回路１１から分岐したパイロット 回路１２により優先バルブ５はばね１３に押されａ位置に切り換えられ、大容量 低圧ポンプ３の吐出油は小容量高圧ポンプ１の吐出油と合流する。その結果、ク ラッチ回路２の油圧は低下するが、クラッチ作動フィル油として補充される。そ して変速機のクラッチ作動が完了すると、クラッチ回路２の油圧は上昇するので 、優先バルブ５はばね１３に抗してｂ位置に切り換えられ、大容量低圧ポンプ３ の吐出油は潤滑回路４に流れて再び、変速機の潤滑専用として使用される。この 場合、従来の油圧ポンプの吐出量が例えば２５０ｌ／ｍｉｎに対して、本考案の 小容量高圧ポンプ１は７０ｌ／ｍｉｎ，大容量低圧ポンプ３は１８０ｌ／ｍｉｎ （合計２５０ｌ／ｍｉｎ）とすると、従来の必要駆動馬力２１．１馬力に対して 、本考案ではポンプ１，３の順に５．９馬力、１．１馬力となり合計しても７馬 力だけとなる。なお、変速機全体の伝動効率への寄与は約２％の改善向上が期待 できる。Next, the operation will be described. The discharge oil (low pressure) of the small capacity high pressure pump 1 and the large capacity low pressure pump 3 driven by the drive motor 7 is used for the transmission lubrication from the transmission lubrication valve 9 through the clutch circuit 2 and the lubrication circuit 4, respectively. However, in this state, the priority valve 5 is in the position a due to the spring 13, and therefore the discharge oil of the large capacity low pressure pump 3 flows through the priority valve 5 to the downstream side of the lubrication circuit 4 to cause the transmission. Lubricated. Next, when the clutch is operated to switch the transmission for forward or backward or for shifting, the oil discharged from the small capacity high pressure pump 1 (high pressure) flows to the clutch 10 and the oil pressure decreases until the clutch piston is filled. The priority valve 5 is pushed by the spring 13 to be switched to the a position by the pilot circuit 12 branched from the above, and the discharge oil of the large capacity low pressure pump 3 joins with the discharge oil of the small capacity high pressure pump 1. As a result, the oil pressure in the clutch circuit 2 drops, but it is replenished as clutch operating fill oil. Then, when the clutch operation of the transmission is completed, the hydraulic pressure of the clutch circuit 2 rises, so the priority valve 5 is switched to the b position against the spring 13, and the discharge oil of the large capacity low pressure pump 3 is lubricated by the lubricating circuit 4. Then, it is used again only for the lubrication of the transmission. In this case, assuming that the discharge amount of the conventional hydraulic pump is 250 l / min, the small capacity high pressure pump 1 of the present invention is 70 l / min, and the large capacity low pressure pump 3 is 180 l / min (total 250 l / min), In contrast to the conventional required driving horsepower of 21.1 horsepower, in the present invention, the pumps 1 and 3 are in order of 5.9 horsepower and 1.1 horsepower, and the total is only 7 horsepower. The contribution to the transmission efficiency of the entire transmission can be expected to improve by about 2%.
【００１１】[0011]
以上説明したように本考案は、クラッチ作動用の小容量高圧ポンプをクラッチ 回路に接続し、潤滑用の大容量低圧ポンプを潤滑回路に接続した変速機の油圧回 路において、該潤滑回路にクラッチ作動時、クラッチ回路の油圧により切り換え られて大容量低圧ポンプの吐出油をクラッチ回路に供給する優先バルブを設ける と共に、前記クラッチ回路と潤滑回路とをクラッチ作動用のリリ−フバルブを介 して接続したから、クラッチ作動油量と潤滑油量の配分が適切となりポンプの必 要駆動馬力は約１／３に低減でき、有効馬力伝達を増加できる。 As described above, according to the present invention, in the hydraulic circuit of the transmission in which the small capacity high pressure pump for clutch operation is connected to the clutch circuit and the large capacity low pressure pump for lubrication is connected to the lubrication circuit, the clutch is connected to the lubrication circuit. During operation, a priority valve that supplies oil discharged from the large-capacity low-pressure pump to the clutch circuit by switching the hydraulic pressure of the clutch circuit is provided, and the clutch circuit and the lubrication circuit are connected via a relief valve for clutch operation. Therefore, the distribution of the amount of clutch operating oil and the amount of lubricating oil becomes appropriate, and the required driving horsepower of the pump can be reduced to about 1/3 and the effective horsepower transmission can be increased.
【図面の簡単な説明】[Brief description of drawings]
【図１】本考案にかかるクラッチ作動優先の変速機油圧
回路の一実施例の説明図である。FIG. 1 is an explanatory view of an embodiment of a transmission hydraulic circuit with a clutch operation priority according to the present invention.
【図２】従来の変速機油圧回路の一例を示す説明図であ
る。FIG. 2 is an explanatory diagram showing an example of a conventional transmission hydraulic circuit.
１ 小容量高圧ポンプ ２ クラッチ回路 ３ 大容量低圧ポンプ ４ 潤滑回路 ５ 優先バルブ ６ リリ−フバルブ 1 Small capacity high pressure pump 2 Clutch circuit 3 Large capacity low pressure pump 4 Lubrication circuit 5 Priority valve 6 Relief valve
Claims (1)
ラッチ回路に接続し、潤滑用の大容量低圧ポンプを潤滑
回路に接続した変速機の油圧回路において、該潤滑回路
にクラッチ作動時、クラッチ回路の油圧により切り換え
られて大容量低圧ポンプの吐出油をクラッチ回路に供給
する優先バルブを設けると共に、前記クラッチ回路と潤
滑回路とをクラッチ作動用のリリ−フバルブを介して接
続したことを特徴とするクラッチ作動優先の変速機油圧
回路。1. A hydraulic circuit of a transmission, wherein a small capacity high pressure pump for clutch operation is connected to a clutch circuit, and a large capacity low pressure pump for lubrication is connected to a lubrication circuit. Is provided with a priority valve that is switched by the hydraulic pressure to supply the discharge oil of the large-capacity low-pressure pump to the clutch circuit, and the clutch circuit and the lubrication circuit are connected via a relief valve for clutch operation. Transmission hydraulic circuit with clutch operation priority.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8249891U JPH0527423U (en) | 1991-09-13 | 1991-09-13 | Transmission hydraulic circuit with priority to clutch operation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8249891U JPH0527423U (en) | 1991-09-13 | 1991-09-13 | Transmission hydraulic circuit with priority to clutch operation |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0527423U true JPH0527423U (en) | 1993-04-09 |
Family
ID=13776161
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8249891U Pending JPH0527423U (en) | 1991-09-13 | 1991-09-13 | Transmission hydraulic circuit with priority to clutch operation |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0527423U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008101778A (en) * | 2006-10-18 | 2008-05-01 | United Technol Corp <Utc> | Planetary gear device and turbine engine |
| JP2010138924A (en) * | 2008-12-09 | 2010-06-24 | Komatsu Ltd | Hydraulic system for working vehicle, and method of controlling the hydraulic system |
| KR101500417B1 (en) * | 2014-10-23 | 2015-03-12 | 현대자동차주식회사 | Oil pressure supply system of automatic transmission |
| JP5896041B2 (en) * | 2012-12-19 | 2016-03-30 | 株式会社島津製作所 | Hydraulic circuit and cargo handling vehicle |
| CN107642604A (en) * | 2016-07-20 | 2018-01-30 | 现代自动车株式会社 | Fluid pressure supply system for the dual-clutch transmission of vehicle |
-
1991
- 1991-09-13 JP JP8249891U patent/JPH0527423U/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008101778A (en) * | 2006-10-18 | 2008-05-01 | United Technol Corp <Utc> | Planetary gear device and turbine engine |
| JP2010138924A (en) * | 2008-12-09 | 2010-06-24 | Komatsu Ltd | Hydraulic system for working vehicle, and method of controlling the hydraulic system |
| JP5896041B2 (en) * | 2012-12-19 | 2016-03-30 | 株式会社島津製作所 | Hydraulic circuit and cargo handling vehicle |
| KR101500417B1 (en) * | 2014-10-23 | 2015-03-12 | 현대자동차주식회사 | Oil pressure supply system of automatic transmission |
| CN107642604A (en) * | 2016-07-20 | 2018-01-30 | 现代自动车株式会社 | Fluid pressure supply system for the dual-clutch transmission of vehicle |
| US10428940B2 (en) | 2016-07-20 | 2019-10-01 | Hyundai Motor Company | Hydraulic pressure supply system of dual clutch transmission for vehicle |
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