JPS6114364B2 - - Google Patents
Info
- Publication number
- JPS6114364B2 JPS6114364B2 JP53105687A JP10568778A JPS6114364B2 JP S6114364 B2 JPS6114364 B2 JP S6114364B2 JP 53105687 A JP53105687 A JP 53105687A JP 10568778 A JP10568778 A JP 10568778A JP S6114364 B2 JPS6114364 B2 JP S6114364B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- bearing
- oil
- accumulator
- liquid
- 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
- 230000002706 hydrostatic effect Effects 0.000 claims description 8
- 239000007788 liquid Substances 0.000 claims description 8
- 238000012423 maintenance Methods 0.000 claims description 3
- 239000002184 metal Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
Description
【発明の詳細な説明】
本発明は協働する軸受面間の金属接触を防止す
る如く、ポンプ故障の際の減速時中、静圧軸受に
所要の液圧を維持する装置に関し、軸受の液体供
給システムへ連結されたアキユムレータを備えて
おり、そのアキユムレータに収容する液体に充分
な液圧を維持する為の装置を持つた維持装置に関
する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an apparatus for maintaining a required hydraulic pressure in a hydrostatic bearing during deceleration in the event of a pump failure, so as to prevent metal contact between cooperating bearing surfaces. The present invention relates to a maintenance device comprising an accumulator connected to a supply system and having a device for maintaining sufficient hydraulic pressure in the liquid contained in the accumulator.
静圧軸受では協働する軸受面は、通常、油の圧
力液体の層で隔離される。所要の油圧はポンプシ
ステムで発生される。該軸受は大きい負荷支持能
力と、低摩擦とを有している。しかしながら、低
摩擦は運転中に所要の油圧が常に維持されること
に依存する。圧力が何等かの理由、例えば停電に
よるポンプのモータの停止などで喪失されるとす
れば、金属接触を生じ、従つて、容易に故障に導
き得る協働する軸受面に大きい摩擦を生じ、これ
は、軸受で通常支持される大きい負荷に基づき大
きな損傷を生じ得る。従つて、例えば停電の際に
軸受はその減速時中、即ち、軸受で支持される部
材が停止するまでに要する時間中、充分な圧力油
が供給される様にすることが安全上必要である。 In hydrostatic bearings cooperating bearing surfaces are separated by a layer of pressure fluid, usually oil. The required hydraulic pressure is generated by a pump system. The bearing has a large load carrying capacity and low friction. However, low friction depends on maintaining the required oil pressure at all times during operation. If pressure were to be lost for any reason, such as stopping the pump motor due to a power outage, this would create metal-to-metal contact and therefore high friction on the cooperating bearing surfaces which could easily lead to failure. can cause significant damage due to the large loads normally supported by the bearings. Therefore, for safety reasons, it is necessary to ensure that, during a power outage, for example, the bearing is supplied with sufficient pressure oil during its deceleration, that is, during the time required for the components supported by the bearing to come to a stop. .
この目的に対し、圧力下の油の或る量を蓄積す
ること、例えばピストンアキユムレータに蓄積す
ることは公知である。この場合、アキユムレータ
は原理的にシリンダから成り、軸方向に自由に可
動なピストンが、シリンダ体積を２部分に区分
し、軸受圧力油系統に連通する油はシリンダの１
つの部分に収容され、圧力ガスはシリンダの他の
部分に収容される。自由に可動なピストンの夫々
の側部の油圧とガス圧とは、ピストンを平衡させ
るためにそれ自体自動的に等しくなる。ガスは圧
縮可能なのでガス体積はこれにより、軸受内に伝
播する油圧に応答して変化し、該軸受の圧力は、
軸受の負荷に関連して順次に変化する。このた
め、アキユムレータに収容される油量は軸受の負
荷で生じる変化に応答して変動する。更に、アキ
ユムレータ内の油量は減速時の所要量を充足する
のに常に充分でなければならない。大きな負荷変
動を受ける軸受、例えば圧延機の軸受ではアキユ
ムレータ体積が大きくなければならず、この体積
が非常に僅かな役割りにのみ利用されることを意
味する。従つて、アキユムレータユニツトの価格
は非常に高く、軸受システムの全体の価格の大き
な部分を占める。更に大きなスペースを要す。 For this purpose, it is known to store a certain amount of oil under pressure, for example in a piston accumulator. In this case, the accumulator essentially consists of a cylinder, in which an axially freely movable piston divides the cylinder volume into two parts, the oil communicating with the bearing pressure oil system being in one part of the cylinder.
The pressure gas is contained in the other part of the cylinder. The hydraulic and gas pressures on each side of the freely movable piston automatically equalize themselves in order to balance the piston. Since the gas is compressible, the gas volume will thereby change in response to the hydraulic pressure propagating within the bearing, and the pressure in the bearing will be:
It changes sequentially in relation to the load on the bearing. Therefore, the amount of oil contained in the accumulator varies in response to changes in bearing load. Furthermore, the amount of oil in the accumulator must always be sufficient to meet the requirements during deceleration. In bearings that are subject to large load fluctuations, for example bearings in rolling mills, the accumulator volume must be large, which means that this volume is used for only a very small purpose. Therefore, the price of the accumulator unit is very high and represents a large part of the total price of the bearing system. It requires even more space.
また、ポンプ故障の際に静圧軸受の軸受面間の
金属接触を防止する他のシステム、例えば、停電
後の特定の時間中ポンプを駆動するフライホイー
ルにポンプシステムを連結するシステム、または
静圧軸受の圧力が喪失されるときに作用する様に
なるローラ軸受の様な補助軸受を支持部材に備え
るシステムが提案された。しかしながら、これ等
の装置は、技術的に複雑で高価であると共に、充
分な信頼性を有していないことが多い。 Also, other systems that prevent metal contact between the bearing surfaces of hydrostatic bearings in the event of a pump failure, for example systems that couple the pump system to the flywheel that drives the pump during a certain period of time after a power outage, or hydrostatic Systems have been proposed in which the support member is provided with an auxiliary bearing, such as a roller bearing, which comes into play when the pressure in the bearing is lost. However, these devices are technically complex, expensive and often do not have sufficient reliability.
本発明の目的は比較的小さいアキユムレータに
より充分な信頼性を有して作用すると共に、非常
に大きい軸受圧力変動において作用する本特許請
求の範囲１記載の型式の装置を提供することであ
る。スペースを節減し且つ安全な装置が低価格で
得られる。これは、本発明により、該装置が本特
許請求の範囲１記載の特徴を賦与されることによ
つて達成される。 The object of the invention is to provide a device of the type claimed in claim 1 which operates with sufficient reliability with relatively small accumulators and which operates with very large bearing pressure fluctuations. A space-saving and safe device is obtained at a low cost. This is achieved according to the invention in that the device is endowed with the features according to claim 1.
本発明を図示の実施例を参照して説明する。 The invention will now be described with reference to illustrated embodiments.
第１図には３つの静圧軸受ブロツク２，３，４
で支持された回転可能なリング１を有する軸受が
示されている。ブロツク２，３，４は夫々１つの
モータ８，９を有する２つのポンプ６，７を介し
て油容器５から圧油を供給され、油の流れは容積
式ポンプとして構成される３つの連結された制量
ユニツト１０，１１，１２を備えそれ自体公知の
流量分配部材でブロツク間に分配される。速度表
示器１２ａは充分な量の油がブロツク２，３，４
に常に流れるのを検出する。軸受からの漏洩流
は、好ましくは、図示していない過装置を介し
導かれて容器５へ戻る。油がシステム内で逆流す
るのを阻止するため、一方向弁１３，１４，１
５，１６，１７が各ポンプユニツトの下流に配置
される。 Figure 1 shows three hydrostatic bearing blocks 2, 3, 4.
A bearing is shown having a rotatable ring 1 supported on it. The blocks 2, 3, 4 are supplied with pressure oil from an oil container 5 via two pumps 6, 7 each having one motor 8, 9, the oil flow being controlled by three connected pumps configured as positive displacement pumps. The flow is distributed between the blocks by means of flow distribution elements known per se. The speed indicator 12a has a sufficient amount of oil in the blocks 2, 3, 4.
Detects constant flow. The leakage flow from the bearing is preferably directed back to the container 5 via a not shown sieve device. One-way valves 13, 14, 1 are installed to prevent oil from flowing back into the system.
5, 16 and 17 are arranged downstream of each pump unit.
ポンプ６，７の故障の際の軸受の減速時間中、
圧力下の油がブロツク２，３，４に供給されるの
を保証するアキユムレータはシリンダ１８を備
え、シリンダ１８の体積は軸方向へ自由に可動な
ピストン１９で２つのチヤンバに区分される。ピ
ストン１９が自由に移動可能なため、圧力は２つ
のチヤンバ内で常に等しい。１つのチヤンバ２０
内には押込ガスが収容され、該チヤンバは、好ま
しくは、ガスが常に充分な圧力を有するのを保証
する如く、特定の押込ガス容器２１に連結され
る。他のチヤンバ２２は、下記で説明する態様に
おいて軸受の圧油系統に連結され、油で充満され
ている。軸受にポンプ６，７から流れる油の一部
は、第１図の実施例では流量分配部材の附加的な
制量ユニツト２３である特定の圧力発生部材を介
して導かれ、このとき、油は軸受に現われる最大
圧力以上の圧力を与えられる。油は、定流量弁２
４，２５，２６が配置された導管を介して軸受ブ
ロツク２，３，４の夫々の１つに制量ユニツト２
３から導かれる。これ等の弁は制量ユニツト２３
を通る油の一部のみを軸受ブロツク２，３，４に
導く如く設定される。常態運転の際、残部は、流
量分配部材の上流の位置２７に導かれて戻され、
この位置では油圧は制量ユニツト２３の下流より
も低い。制量ユニツト２３から流れる油に所望の
油圧の設定を可能にするため、調節可能な定圧弁
２８は位置２７の上流で戻り導管に挿入される。
弁２８はアキユムレータのチヤンバ２２内の油の
所望の圧力で開口する如く設定される。例えば始
動の際に圧力が低い限り弁２８は閉鎖され、ユニ
ツト２３を通る流量がユニツト２４，２５，２６
を通る流量より多いとき、油の残部はチヤンバ２
２へ流れ、チヤンバ２２は制量ユニツト２３と、
弁２８を有する戻り導管と、軸受ブロツク２，
３，４の定流量弁２４，２５，２６を有する導管
とに連通する。始動の際に油がチヤンバ２２内へ
流れるとき、チヤンバ２２の容積は増大し、これ
により、チヤンバ２０の体積はこれに応じ減少し
てガス圧力が上昇し、従つてチヤンバ２２内の圧
力は上昇する。 During the bearing deceleration time when pumps 6 and 7 fail,
The accumulator, which ensures that oil under pressure is supplied to the blocks 2, 3, 4, comprises a cylinder 18, the volume of which is divided into two chambers by a piston 19 which is freely movable in the axial direction. Since the piston 19 is freely movable, the pressure is always equal in the two chambers. one chamber 20
A forced gas is contained within the chamber, which chamber is preferably connected to a specific forced gas container 21 to ensure that the gas always has sufficient pressure. The other chamber 22 is connected to the bearing's hydraulic system in a manner described below and is filled with oil. A portion of the oil flowing into the bearings from the pumps 6, 7 is directed via a specific pressure-generating element, which in the embodiment of FIG. 1 is an additional restriction unit 23 of the flow distribution element, the oil A pressure greater than the maximum pressure appearing on the bearing is applied. For oil, constant flow valve 2
The metering unit 2 is connected to one of the bearing blocks 2, 3, 4 via a conduit in which the bearing blocks 2, 3, 4 are arranged.
It is derived from 3. These valves are the control unit 23
The arrangement is such that only a portion of the oil passing through the bearing block is guided to the bearing blocks 2, 3, 4. During normal operation, the remainder is guided back to the upstream position 27 of the flow distribution member;
In this position the oil pressure is lower than downstream of the metering unit 23. An adjustable constant pressure valve 28 is inserted in the return conduit upstream of position 27 in order to enable setting of the desired oil pressure in the oil flowing from the metering unit 23.
Valve 28 is set to open at the desired pressure of oil within chamber 22 of the accumulator. For example, during start-up, as long as the pressure is low, valve 28 will be closed and the flow through unit 23 will be limited to units 24, 25, 26.
When the flow rate is greater than the flow rate through chamber 2, the remainder of the oil flows through chamber 2.
2, the chamber 22 is connected to a control unit 23,
a return conduit with a valve 28 and a bearing block 2;
It communicates with a conduit having three and four constant flow valves 24, 25, 26. When oil flows into the chamber 22 during startup, the volume of the chamber 22 increases, which causes the volume of the chamber 20 to correspondingly decrease and the gas pressure to increase, thus increasing the pressure in the chamber 22. do.
圧力が弁２８の設定圧力に達すると弁２８は開
口し、過剰な油はアキユムレータへではなく戻り
導管を流通し、従つて、アキユムレータは運転
中、所望の圧力の油を常に充填される。ポンプ
６，７の故障の際、流量分配部材を通る流れは停
止し、従つて、制量ユニツト２３を通る流れも停
止し、これにより、この下流の圧力は低下する。
弁２８はこれによつて閉じ、油は金属接触がブロ
ツクとリングとの間に現われる程ブロツク２，
３，４における圧力が低くなる前に回転可能なリ
ング１が停止するための時間を有する様な長い時
間中、弁２４，２５，２６を有する導管を介しチ
ヤンバ２０内のガス圧力によりチヤンバ２２から
押出される。逆止弁２９は、油がアキユムレータ
から制量ユニツト２３を介して逆流するのを阻止
する。軸受の最大油圧を越え得る弁２８により、
チヤンバ２２内の油圧を所望の値に設定すること
が可能なため、チヤンバ２２に収容される全体の
油量は例えばポンプの故障の際、所要の圧力で軸
受に供給される。従つて、本発明により、軸受の
減速時の際に軸受に丁度必要な油量を貯蔵するの
に要する以上の如何なる大きさにもアキユムレー
タユニツトを製作することが必要ではない。 When the pressure reaches the set pressure of the valve 28, the valve 28 opens and the excess oil flows through the return conduit rather than to the accumulator, so that the accumulator is always filled with oil at the desired pressure during operation. In the event of a failure of the pumps 6, 7, the flow through the flow distribution member and therefore the flow through the metering unit 23 is also stopped, so that the pressure downstream thereof is reduced.
Valve 28 is thereby closed, and the oil flows into block 2, to such an extent that a metal contact appears between the block and the ring.
During such a long period of time that the rotatable ring 1 has had time to stop before the pressure at 3, 4 drops, the gas pressure in the chamber 20 is removed from the chamber 22 via a conduit with valves 24, 25, 26. Extruded. The check valve 29 prevents oil from flowing back from the accumulator through the metering unit 23. The valve 28 allows the maximum oil pressure of the bearing to be exceeded.
Since the oil pressure in the chamber 22 can be set to a desired value, the total amount of oil accommodated in the chamber 22 is supplied to the bearings at the required pressure, for example in the event of a pump failure. According to the invention, it is therefore not necessary to make the accumulator unit any larger than is necessary to store just the amount of oil required in the bearing during deceleration of the bearing.
ポンプ故障の際の軸受の減速時中、アキユムレ
ータからの或る流量が必要であり、該流量は好ま
しくは、所与の軸受負荷での運転中の常態流量の
少くとも約10％である。この軸受は更に、軸受の
作用中にポンプ／モータユニツトの１台の補修と
手入れとを許容する如く、ポンプ６，７の１つの
みの運転、即ち、半分の流量で制約なしに駆動可
能でなければならない。更に、半分の流量での制
量ユニツト２３を通る油量は軸受への常態流量の
少くとも10％が必要で、即ち、アキユムレータ内
の圧力が維持されるのを確保するのに要するのと
少くとも同量が弁２４，２５，２６を流通するこ
とが必要である。これは、両者のポンプが作動し
ている常態運転ではユニツト２３を通つて圧送さ
れる油の半分以上が戻り導管を流通することを意
味する。しかしながら、全体の油の流量の約25％
のみがユニツト２３を通ることを要するため、弁
２４，２５，２６，２８を介する全体の流量損失
は、むしろ小さい。 During bearing deceleration in the event of a pump failure, a certain flow rate from the accumulator is required, which flow rate is preferably at least about 10% of the normal flow rate during operation at a given bearing load. This bearing furthermore allows operation of only one of the pumps 6, 7, i.e. at half flow rate, without restriction, so as to allow repairs and maintenance of one of the pump/motor units while the bearing is in operation. There must be. Furthermore, the amount of oil through the metering unit 23 at half flow rate is required to be at least 10% of the normal flow rate to the bearing, i.e. less than that required to ensure that the pressure in the accumulator is maintained. It is necessary that the same amount of both flows through the valves 24, 25, and 26. This means that in normal operation, with both pumps running, more than half of the oil pumped through the unit 23 will flow through the return conduit. However, about 25% of the total oil flow
The overall flow loss through the valves 24, 25, 26, 28 is rather small since only the flow rate required to pass through the unit 23.
第２図には、本発明の装置の他の一実施例が示
されている。軸受と液圧システムは第１図とほゞ
同一の構成を有しているが、特定の圧力発生部材
はこの実施例ではポンプユニツト３２，３３とし
て構成され、該ポンプユニツトは、流量分配部材
３４の附加的な制量ユニツトの代りに主ポンプ３
０，３１に連結される。この装置のその他の要素
は、第１図に示されたものに完全に対応し、この
装置は、対応する態様で運転される。 FIG. 2 shows another embodiment of the device of the invention. The bearings and hydraulic system have substantially the same construction as in FIG. main pump 3 instead of an additional metering unit
Connected to 0,31. The other elements of the device correspond completely to those shown in FIG. 1, and the device is operated in a corresponding manner.
本発明は図示の実施例に限定されることなく特
許請求の範囲に記載された技術思想に則り種々に
変更して実施することができる。例えば、唯一の
軸受ブロツクが使用されるとすれば、流量分配部
材は必要ではなく、従つて、好ましくは、特定の
圧力発生部材と軸受ブロツクとの間の導管に唯一
の定流量弁が使用される。上述の型式の流量分配
部材の代りに、その他のシステム、例えば絞りを
各軸受ブロツクに連結された導管に使用すること
は勿論可能である。また、夫々流量分配部材を構
成する第１図のポンプ１０，１１，１２，２３
と、第２図の３４に対し特定の駆動モータを配置
することも可能である。 The present invention is not limited to the illustrated embodiments, but can be implemented with various modifications in accordance with the technical idea described in the claims. For example, if only one bearing block is used, no flow distribution member is necessary and therefore preferably only one constant flow valve is used in the conduit between a particular pressure generating member and the bearing block. Ru. It is of course possible to use other systems instead of flow distribution elements of the type described above, for example a restriction in the conduit connected to each bearing block. In addition, the pumps 10, 11, 12, 23 of FIG.
It is also possible to place a specific drive motor in place of 34 in FIG.
第１図は本発明の一実施例の模式図、第２図は
同じく他の一実施例の模式図で、図中、１０，１
１，１２は制量ユニツト、１８はアキユムレータ
のシリンダ、１９はピストン、２０は圧力ガスの
チヤンバ、２１は圧力ガス容器、２２は圧油のチ
ヤンバ、２３は附加的な制量ユニツト、２４，２
５，２６は定流量弁、２７は低い圧力の位置、２
８は定圧弁、３２，３３はポンプユニツトを示
す。
FIG. 1 is a schematic diagram of one embodiment of the present invention, and FIG. 2 is a schematic diagram of another embodiment.
1 and 12 are control units, 18 are cylinders of the accumulator, 19 are pistons, 20 are pressure gas chambers, 21 are pressure gas containers, 22 are pressure oil chambers, 23 are additional control units, 24, 2
5, 26 are constant flow valves, 27 is a low pressure position, 2
8 is a constant pressure valve, and 32 and 33 are pump units.
Claims (1)
一部を静圧軸受の最高液圧以上の圧力に加圧する
特定の圧力発生部材と、 圧力発生部材が加圧した圧力液体の一部を軸受
に導く定流量弁と、 圧力発生部材が加圧した圧力液体と通じ、内部
の液圧を上記圧力液体の液圧と同等の圧力に維持
するアキユムレータと、 上記アキユムレータの内部の液圧が軸受の最高
液圧以上のときに開き、それよりも低いときには
閉じる調整可能な一方向弁と、 上記アキユムレータに通じた圧力液体を、上記
一方向弁が開いたときに低圧に維持される液体供
給系中に連結する戻し導管と を備えていることを特徴とする静圧軸受に所要
の液圧を維持する維持装置。[Scope of Claims] 1. A specific pressure generating member that pressurizes a portion of the pressure liquid supplied to the hydrostatic bearing by the liquid supply system to a pressure higher than the maximum liquid pressure of the hydrostatic bearing; and a pressure generating member pressurized. a constant flow valve that guides a portion of the pressurized liquid to the bearing; an accumulator that communicates with the pressurized liquid pressurized by the pressure generating member and maintains the internal hydraulic pressure at the same pressure as the hydraulic pressure of the pressurized liquid; an adjustable one-way valve that opens when the internal hydraulic pressure is equal to or higher than the maximum hydraulic pressure of the bearing and closes when it is lower; A maintenance device for maintaining a required hydraulic pressure in a hydrostatic bearing, comprising: a return conduit connected to a maintained liquid supply system.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE7709826A SE416075B (en) | 1977-09-01 | 1977-09-01 | DEVICE FOR MAINTENANCE OF REQUIRED LIQUID PRINTING IN A HYDROSTATIC STOCK |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5447054A JPS5447054A (en) | 1979-04-13 |
| JPS6114364B2 true JPS6114364B2 (en) | 1986-04-18 |
Family
ID=20332147
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10568778A Granted JPS5447054A (en) | 1977-09-01 | 1978-08-31 | Apparatus for maining required liquid pressure for static bearing |
Country Status (12)
| Country | Link |
|---|---|
| JP (1) | JPS5447054A (en) |
| AT (1) | AT382442B (en) |
| AU (1) | AU519128B2 (en) |
| BR (1) | BR7805699A (en) |
| CA (1) | CA1094620A (en) |
| DE (1) | DE2837346C3 (en) |
| FI (1) | FI65651C (en) |
| FR (1) | FR2402102A1 (en) |
| GB (1) | GB2003559B (en) |
| NO (1) | NO146407C (en) |
| SE (1) | SE416075B (en) |
| ZA (1) | ZA784955B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3151001C2 (en) * | 1981-12-23 | 1986-04-24 | Kleinewefers Gmbh, 4150 Krefeld | Hydrostatically mounted roller, in particular pressure treatment roller |
| DE3660115D1 (en) * | 1985-06-10 | 1988-05-05 | Interatom | Aerostatic bearing having a double conical configuration |
| JPS62127512A (en) * | 1985-11-29 | 1987-06-09 | Hitachi Seiko Ltd | Power failure backup unit for air bearing |
| CN111637159A (en) * | 2020-05-18 | 2020-09-08 | 哈尔滨工程大学 | Self-adaptive forced lubrication bearing with pressurizing hole |
| CN111637161B (en) * | 2020-05-18 | 2021-11-09 | 哈尔滨工程大学 | Forced lubrication bearing with distributed pores |
| CN111637160B (en) * | 2020-05-18 | 2021-11-05 | 哈尔滨工程大学 | Forced lubrication bearing with uneven aperture |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1525813A1 (en) * | 1966-10-18 | 1969-07-31 | Rexroth Gmbh G L | Circuit for a hydraulic system with a fluid reservoir |
| DE1600333A1 (en) * | 1967-02-03 | 1970-06-04 | Linde Ag | Pneumatic relubrication device for flow machines |
| FR2004064A1 (en) * | 1968-03-16 | 1969-11-21 | Hoechst Ag | |
| SE340200B (en) * | 1970-06-12 | 1971-11-08 | Skf Ind Handel En Onwikkeling | |
| US4002224A (en) * | 1975-02-26 | 1977-01-11 | Westinghouse Electric Corporation | Turbine lubrication and emergency gas system |
-
1977
- 1977-09-01 SE SE7709826A patent/SE416075B/en not_active IP Right Cessation
-
1978
- 1978-08-22 FI FI782563A patent/FI65651C/en not_active IP Right Cessation
- 1978-08-26 DE DE2837346A patent/DE2837346C3/en not_active Expired
- 1978-08-30 AU AU39370/78A patent/AU519128B2/en not_active Expired
- 1978-08-30 FR FR7825089A patent/FR2402102A1/en active Granted
- 1978-08-30 ZA ZA00784955A patent/ZA784955B/en unknown
- 1978-08-31 BR BR7805699A patent/BR7805699A/en unknown
- 1978-08-31 JP JP10568778A patent/JPS5447054A/en active Granted
- 1978-08-31 CA CA310,420A patent/CA1094620A/en not_active Expired
- 1978-08-31 NO NO782966A patent/NO146407C/en unknown
- 1978-09-01 AT AT0634378A patent/AT382442B/en not_active IP Right Cessation
- 1978-09-01 GB GB7835395A patent/GB2003559B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| AT382442B (en) | 1987-02-25 |
| SE7709826L (en) | 1979-03-02 |
| CA1094620A (en) | 1981-01-27 |
| GB2003559A (en) | 1979-03-14 |
| DE2837346C3 (en) | 1982-01-28 |
| ATA634378A (en) | 1986-07-15 |
| FI782563A (en) | 1979-03-02 |
| FI65651B (en) | 1984-02-29 |
| DE2837346B2 (en) | 1981-05-27 |
| SE416075B (en) | 1980-11-24 |
| DE2837346A1 (en) | 1979-03-08 |
| ZA784955B (en) | 1979-08-29 |
| FR2402102B1 (en) | 1983-11-04 |
| NO146407B (en) | 1982-06-14 |
| AU3937078A (en) | 1980-03-06 |
| JPS5447054A (en) | 1979-04-13 |
| NO146407C (en) | 1982-09-22 |
| GB2003559B (en) | 1982-02-10 |
| FR2402102A1 (en) | 1979-03-30 |
| NO782966L (en) | 1979-03-02 |
| AU519128B2 (en) | 1981-11-12 |
| BR7805699A (en) | 1979-04-17 |
| FI65651C (en) | 1984-06-11 |
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