JPH01310119A - Screw rotor machine controlled by sliding valve and supercharing internal combustion engine with said screw rotor machine - Google Patents
Screw rotor machine controlled by sliding valve and supercharing internal combustion engine with said screw rotor machineInfo
- Publication number
- JPH01310119A JPH01310119A JP1019926A JP1992689A JPH01310119A JP H01310119 A JPH01310119 A JP H01310119A JP 1019926 A JP1019926 A JP 1019926A JP 1992689 A JP1992689 A JP 1992689A JP H01310119 A JPH01310119 A JP H01310119A
- Authority
- JP
- Japan
- Prior art keywords
- sliding valve
- rotor machine
- screw rotor
- screw
- suction
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 19
- 230000000149 penetrating effect Effects 0.000 claims description 2
- 241001417968 Polynemidae Species 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 4
- 230000001419 dependent effect Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000002459 sustained effect Effects 0.000 description 1
- 239000002966 varnish Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
- F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/36—Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、吸入路に配置された圧縮機を持つ過ＦｊＲ燃
ＲｒＭＩに関する。本発明はさらに、前述のような内燃
機関に特に過給器として使用できる、摺動弁で制御され
るねじ回転子機械に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a super-FjR fuel RrMI with a compressor arranged in the suction passage. The invention furthermore relates to a screw rotor machine controlled by a sliding valve, which can be used in particular as a supercharger in an internal combustion engine as described above.
内燃機関における過給のために、すなわち燃焼用空気の
前圧縮のために様々な構造様式の圧＠今・トリわけねじ
回転子機械（以下ねじ圧縮機という）が考慮の対象にな
る。しかし従来公知のねじ圧縮機は、過給器として使用
するには簡単には適していない。なぜならばこの場合は
いくつかの欠点が生ずるからである。For supercharging in internal combustion engines, that is to say for precompressing the combustion air, various types of pressure-divided screw rotor machines (hereinafter referred to as screw compressors) come into consideration. However, previously known screw compressors are not easily suitable for use as superchargers. This is because several drawbacks arise in this case.
絞り運転及び圧縮運転中に機関の燃焼用空気が過給器に
通される場合は、両方の運転方法において過給器出力が
機関のクランク軸から取り出されなければならない。絞
り運転中ではさらに、過給器の後に機関の所要吸入圧力
を供給できるようにするために、過給器の前の圧力が過
給器の組み込まれた圧力比に応じて低下されなければな
らない。この圧力低下は比較的高い損失出力をもたらし
、この損失出力は機関により補われなければならない。If engine combustion air is passed through a supercharger during throttling and compression operations, the supercharger power must be taken from the engine crankshaft in both operating modes. In addition, during throttling operation the pressure before the supercharger must be reduced according to the built-in pressure ratio of the supercharger in order to be able to supply the required suction pressure of the engine after the supercharger. . This pressure drop results in a relatively high power loss, which must be compensated by the engine.
絞り運転状頓で過給器が例えばバイパスにより迂回され
かつ、かなりの制御及び構成費用を必要とすることであ
るが、圧縮運転中にはじめて継手を介して接続される場
合は、過給器の接続の際に同期化伝動装置の急激なトル
ク上昇が起こる。If the turbocharger is bypassed, for example by a bypass, in throttle operation and is connected via a coupling for the first time during compression operation, which requires considerable control and construction costs, the turbocharger During connection, a sudden torque increase of the synchronized transmission occurs.
さらに機関は依然として、絞り弁に生ずる損失を補わな
ければならない。Furthermore, the engine still has to compensate for losses occurring in the throttle valve.
特許請求の範ｆ第２項の上位概念に挙げられたような、
摺動弁で制御されるねじ回転子機械は、ドイツ連邦共和
国待許出顆公告第１２９３３８４号明細齋から公知であ
る。この場合、慴動弁の軸線方向変位によって、互いに
かみ合う回転子及びハウジング壁により包囲される圧縮
隔壁が低圧入口から分離する時点を変えることができ、
それによって機械の流量出力又は定格圧力比を変えるこ
とができる。しかしこの場合、ねじ回転子機械の吸入断
面を単に変えることはできるが、しかし完全には閉鎖す
ることができない。As listed in the generic concept of patent claim f(2),
A screw rotor machine controlled by a sliding valve is known from German Publication No. 1293384. In this case, by axial displacement of the sliding valve, the point at which the compression bulkhead surrounded by the intermeshed rotor and the housing wall separates from the low-pressure inlet can be varied;
Thereby, the flow output or rated pressure ratio of the machine can be varied. In this case, however, the suction cross-section of the screw rotor machine can simply be changed, but it cannot be completely closed.
従ってこのような機械を内燃機関の過給器として使用す
る場合は、内燃機関の吸入量を変えるための付加的な絞
り機構、例えば通常の絞り弁、が依然として必要である
。When such machines are used as a supercharger for an internal combustion engine, an additional throttle mechanism, for example a conventional throttle valve, is therefore still necessary for varying the intake quantity of the internal combustion engine.
〔発明が解決しようとする課題Ｊ
本発叫の諜萌は、過給内燃機関と、大きな構成及び制ｌ
ｌＩＩＩ費用なしに絞り運転中に生ずる、過給器及び従
来必要な絞り弁の損失を減少させるこのような機関用の
過給器として使用可能なねじ回転子機械とを提供するこ
とである。さらに、絞り運転状蝮から過給状部への移行
の際の機関の持続的なトルク経過が得られなければなら
ない。[Problem to be solved by the invention J] The secret of this proposal is the supercharged internal combustion engine and its large configuration and controllability.
It is an object of the present invention to provide a screw rotor machine which can be used as a supercharger for such an engine, reducing the losses of the supercharger and the previously required throttle valve that occur during throttling operation without any expense. Furthermore, a sustained torque profile of the engine during the transition from the throttling mode to the supercharging mode must be achieved.
この牒軛は本発明によれば、圧縮機がねじ回転子機械と
して構成されかつ吸入側に摺動弁を持ち、この摺動弁に
よりねじ回転子機械の吸入絞り機構でありかつ加速ペダ
ルなどにより機関の出力制作部材が操作可能であること
を特徴とする、吸入路に配置された圧縮機を持つ過給内
燃機関又は低圧接続管片と動作空間との接続部が摺動弁
により完全に閉鎖可能であることを特徴とする、ねじひ
れとねじ溝が互いにかみ合う少なくとも２つのねじ回転
子が、互いに貫通する、軸線に対して平行なシリンダ孔
により形成されかつ端壁により区画されたハウジングの
動作空間内に配置され、このハウジングが、＠作中間へ
開口している低圧接続管片と高圧接続管片及び回転子軸
線に対して平行に移動可能に設けられた摺の弁を持ち、
この摺動弁が、低圧接続管片に対応する側に動作空間の
周壁の一部を形成しかつ摺動弁の位置に応じて低圧接続
管片から動作空間内への流れ通路を多かれ少なかれ開放
する、特に過給器として使用される、摺動弁で制御され
るねじ回転子機械によって解決される。それ以外の′有
利な構成は特許請求の範囲の実＠態様項に示されている
。According to the present invention, the compressor is configured as a screw rotor machine and has a slide valve on the suction side, and this slide valve serves as the suction throttle mechanism of the screw rotor machine, and the accelerator pedal etc. A supercharged internal combustion engine with a compressor arranged in the suction duct, characterized in that the power-producing parts of the engine are operable, or the connection between the low-pressure connection piece and the working space is completely closed by means of a sliding valve. Operation of a housing characterized in that at least two screw rotors whose screw fins and screw grooves are intermeshing with each other are formed by mutually penetrating cylinder bores parallel to the axis and delimited by end walls. The housing is disposed in the space, and has a low pressure connecting pipe piece and a high pressure connecting pipe piece opening to the workpiece, and a sliding valve movably provided in parallel to the rotor axis;
This sliding valve forms part of the peripheral wall of the working space on the side corresponding to the low-pressure connecting piece and, depending on the position of the sliding valve, opens more or less a flow path from the low-pressure connecting piece into the working space. is solved by a screw rotor machine controlled by a sliding valve, in particular used as a supercharger. Other advantageous configurations are indicated in the dependent claims.
本発明の核心は、在来の吸入機関の絞り弁の代わりに、
ねじ圧縮機の吸入側に設けられた摺動弁を使用しかつ適
当に操作すべき教示である。The core of the invention is that instead of the throttle valve of a conventional suction engine,
This teaching teaches how to use and properly operate a sliding valve on the suction side of a screw compressor.
本発明の実施例を図面により詳細に説明する。 Embodiments of the present invention will be described in detail with reference to the drawings.
第１図ないし第３図に示したねじ回転子機械ｌは、ねじ
ひれ回転子又は主回転子２と、ねじ溝回転子又は副回転
子３とを持っており、これらは軸線に対して平行にかつ
互いにかみ合って、互いに交差する２つの円筒により形
成されたハウジング１３の動作空間内に配置されている
。The screw rotor machine l shown in Figures 1 to 3 has a screw fin rotor or main rotor 2 and a screw groove rotor or auxiliary rotor 3, which are parallel to the axis. The housing 13 is disposed in a working space of a housing 13 formed by two cylinders that interlock with each other and intersect with each other.
実施例では主回転子２が駆動され、この駆動は同期化歯
車１０及び９を介して副回転子３へ伝達される。しかし
副回転子３を駆動することも可能であり、さらに同期化
伝動装置１０，９を省くことができかつ駆動を直接、互
いにかみ合う回転子歯面を介して一方の回転子から他方
の回転子へ伝達することができる。In the exemplary embodiment, the main rotor 2 is driven, and this drive is transmitted to the auxiliary rotor 3 via synchronization gears 10 and 9. However, it is also possible to drive the auxiliary rotor 3, and also to dispense with the synchronizing gears 10, 9, and to transfer the drive directly from one rotor to the other via the mutually meshing rotor tooth flanks. can be transmitted to.
ハウジング１３の動作空間へ、一方のハウジング側にお
いて吸入接続管片７が開口し、他方のハウジング側にお
いて吐出Ｗ！続管片８が開口している。ハウジングの動
作空間は、吸入接続管片に対応する端部において低圧側
のｗＪ乍空間端壁１２により閉鎖されかつ吐出接続管片
８に対応する端部において高圧側の動作空間端壁１１に
より閉鎖されている。The suction connection pipe 7 opens into the working space of the housing 13 on one housing side, and the discharge W! on the other housing side. The continuation tube piece 8 is open. The working space of the housing is closed at the end corresponding to the suction connection piece by a low-pressure side wJ space end wall 12 and at the end corresponding to the discharge connection piece 8 by a high-pressure side working space end wall 11. has been done.
吸入接続管片７に近い方のハウジング側では、動作空間
の８壁が両方の円筒の交差範囲において、軸線方向に移
動可能に案内される慴動弁４により形成される。摺動弁
４の軸線方向変位により、吸入接続管片７とハウジング
１３の動作空間との接続部を完全に閉鎖することができ
又は多かれ少なかれ開放することができる。閉・鎖方向
に見て前方に位置する端面に摺動弁４は、第２図の線４
ａによって示されているばち影輪郭を持っており、この
輪郭は、摺動弁開口の範囲における互いにかみ合う２つ
の主及び副回転子ひれの螺旋状歯先線又は稜線の経過に
合わされている。摺動弁４がこのばち形に切り欠かれた
端面にも拘らず吸入接続管片７との接続部を完全に閉鎖
することができるようにするために、摺動弁４は、この
摺動弁４の端面の三角形により生ずる吸入接続管片７と
動作空間との間の開口も閉鎖されるまで、動作空間の低
圧側端壁１２を越えて移動できなければならない。第２
図に、完全に閉鎖された位置における慴動弁４の端面の
位置が破線４ｂにより示されている。従って動作空間の
低圧側端壁１２は、摺動弁４の完全な閉鎖運動を許容す
る切欠き又はポケットを持っていなければならず、他方
、摺動弁の開放運動は高圧側の端壁ｌｌにある切欠きに
より可能にされる。On the side of the housing closest to the suction connection piece 7, the eight walls of the working space are formed by a sliding valve 4 which is axially movably guided in the area of intersection of the two cylinders. By axially displacing the sliding valve 4, the connection between the suction connection piece 7 and the working space of the housing 13 can be completely closed or more or less opened. The sliding valve 4 on the end face located forward when viewed in the closing/closing direction is aligned with the line 4 in FIG.
It has a dowel profile indicated by a, which profile is adapted to the course of the helical tip lines or ridges of the two intermeshed primary and secondary rotor fins in the area of the sliding valve opening. . In order for the sliding valve 4 to be able to completely close the connection with the suction connection piece 7 despite this dovetail-shaped end face, the sliding valve 4 is The opening between the suction connection piece 7 and the working space, which is created by the triangular shape of the end face of the valve train 4, must also be able to move beyond the low-pressure end wall 12 of the working space until it is closed. Second
In the figure, the position of the end face of the sliding valve 4 in the fully closed position is indicated by a broken line 4b. The low-pressure end wall 12 of the working space must therefore have a cutout or pocket that allows a complete closing movement of the sliding valve 4, while the opening movement of the sliding valve is restricted to the high-pressure end wall ll. This is made possible by the notch in the.
摺動弁４は、その内部に配置されたコイルはね５により
自動的に閉鎖位置に押し付けられる。The sliding valve 4 is automatically pushed into the closed position by a coil spring 5 arranged inside it.
この摺動弁をはね５の力に抗して引張装置１ｉ６、例え
ばボーデンケーブル、により開放方向に移動させること
ができ、それによって吸入接続管片７と動作空間との接
続を多かれ少なかれ、必要な場合には完全な最大値まで
、開放することができる。This sliding valve can be moved in the opening direction against the force of the spring 5 by means of a tensioning device 1i6, for example a Bowden cable, so that the connection between the suction connection piece 7 and the working space can be made more or less necessary. In certain cases, it can be opened to the full maximum value.
第４図は、例えば４気筒内燃機関２０の空気濾過器１７
からシリンダ空間へ至る空気吸入系における過給器とし
てのねじ回転子機械１の配置を概略的に示している。空
気濾過器１７から来る過給器ｌの吸入管路は１８で示さ
れており、この過・給器により作用を受ける、内燃機関
２０へ至る吸入管路は１９で示されている。過給器！は
、例えばベルト駆動装置２２を介して機関２０のクラン
ク軸により駆動される。２３は、内＠機関の排気管路で
ある６過給器ｌの摺動弁４は引張袋Ｒ６を介して内燃機
関２０の加速ペダル２１により制御される。摺動弁４に
より制御される開口及び過給器１の機械による瀾れ間隙
部を介する以外に、吸入管路１８から過給器１の動作空
間への接続及びそこから過給器１により作用を受ける管
路への接続はない。さらに、り機構は設けられていない
。摺動弁４は絞り弁の機能を引き受けるので、この摺動
弁は例えば加速ペダル２１を介して開放されかつ加速ペ
ダルの釈放の際にはね５（＠１図ンにより自動的に１１
５ｍＩｍされる。これらすべての１ｆｌｌａ体の組み合
わせにより、制御されるねじ回転子機械１を圧縮機（摺
動弁４は完全開宸）としてかつ複合膨張機−圧＠橢（摺
動弁４は部分的開放又は閉鎖）として運転することがで
きる。FIG. 4 shows, for example, an air filter 17 of a four-cylinder internal combustion engine 20.
1 schematically shows the arrangement of a screw rotor machine 1 as a supercharger in an air intake system leading from to the cylinder space. The intake line of the supercharger l coming from the air filter 17 is designated by 18, and the intake line leading to the internal combustion engine 20, which is served by this supercharger, is designated by 19. Supercharger! is driven by the crankshaft of the engine 20 via a belt drive device 22, for example. 23 is an exhaust pipe of the internal combustion engine 6. The sliding valve 4 of the supercharger 1 is controlled by the accelerator pedal 21 of the internal combustion engine 20 via a tension bag R6. In addition to the opening controlled by the sliding valve 4 and the mechanical stagnation gap of the supercharger 1, there is also a connection from the suction line 18 to the working space of the supercharger 1 and from there an action by the supercharger 1. There is no connection to the receiving conduit. Furthermore, no mechanism is provided. The sliding valve 4 assumes the function of a throttle valve, so that it can be opened, for example, via the accelerator pedal 21 and is automatically activated by the spring 5 when the accelerator pedal is released.
5mIm will be given. The combination of all these bodies allows the controlled screw rotor machine 1 to be used as a compressor (sliding valve 4 is fully open) and as a compound expander - pressure @ (sliding valve 4 is partially open or closed). ) can be driven as.
膨張機としての運転は、ｉａ咋空間がねじ回転子機械ｌ
の吸入側で吐出側とまったく同じように気密である場合
にのみ７ｉ４切に可能である。この気密は、第３図に示
されているように、回転子歯の前及び後歯面の、好まし
いことにサイクロイドから形成された同じ形状により達
成される。When operating as an expander, the space is a screw rotor machine.
This is only possible if the suction side is just as airtight as the discharge side. This tightness is achieved by the same shape of the front and rear tooth flanks of the rotor teeth, preferably formed from cycloids, as shown in FIG.
絞り運転中に仕事を回収することができる、この制御さ
れるねじ過給器の動作方法を、第５図の容積曲線及び第
６図のＰ−Ｖ線図により説明する。The method of operation of this controlled screw supercharger, which allows work to be recovered during throttling operation, is explained by means of the volume curve in FIG. 5 and the P-V diagram in FIG. 6.
在来のねじ過給器は空気を吸入し、最大隔室容積（第１
図の点２）に達した際に動作空間を閉鎖し、排出側ｗＪ
縁に達するまで容積を縮小しく第１図の点２）、その後
空気を押し出し、他方、制御されるねじ過給器の場合に
は、吸入空間に対する動作空間の閉鎖を、摺動弁位置に
応じて、最小隔室容積（点りと最大隔室容積（点Ｚ）と
の間で変化させることができる。Conventional screw superchargers suck air and have a maximum compartment volume (first
When point 2) in the figure is reached, the operating space is closed and the discharge side wJ
The volume is reduced until the edge is reached (point 2 in Figure 1) and then the air is forced out, while in the case of controlled screw superchargers the closing of the working space to the suction space is dependent on the sliding valve position. can be varied between the minimum compartment volume (point Z) and the maximum compartment volume (point Z).
制ＭＪ摺動弁が部分的に閉鎖されている場合は、第６図
の曲線Ｉに応じた状態経過が生ずる。容積Ｖ、に達した
際は、動作空間が周囲に対して閉鎖される。それに続い
て、吸入された空気は、最大隔室容積ｖ０工が得られる
まで膨張せしめられる。第６区に点を施された面は、膨
張により生ぜしめられる仕事である。最大隔室容積に達
した後に、空気は、組み込まれた制ＭＪ隊により予め設
定された容積ｖ２に達するまで、圧縮される。If the control MJ sliding valve is partially closed, a state sequence according to curve I in FIG. 6 occurs. When the volume V is reached, the working space is closed to the surroundings. Subsequently, the inhaled air is expanded until the maximum compartment volume v0 is obtained. The dotted area in the 6th section is the work produced by expansion. After reaching the maximum compartment volume, the air is compressed until a preset volume v2 is reached by the built-in MJ force.
圧縮により吸収される仕事は、第６図にハツチングをさ
れた面に相当する。The work absorbed by compression corresponds to the hatched area in FIG.
制御されるねじ過給器により回収される仕事は、第６１
ｍノＰ−Ｖ ＃Ｗノ点Ａ−Ｂ−Ｃ−Ｄ １７）間の面に
相当する。The work recovered by the controlled screw supercharger is
Corresponds to the surface between m no PV and # W no points A-B-C-D 17).
摺動弁が圧縮運転（第６図曲線ＩＩに応じた状態経過）
が完全に開放されている場合には、膨張は行なわれず、
圧縮機により吸取される仕事は、第６図（７）Ｐ−Ｖ線
図における点Ａ−Ｅ−Ｆ−Ｇの間の面に相当する。The sliding valve is in compression operation (state progression according to curve II in Figure 6)
If is completely open, no expansion takes place;
The work absorbed by the compressor corresponds to the plane between points A-E-F-G in the P-V diagram in FIG. 6(7).
絞り弁と摺動弁との取り蓄え及びそれに伴う仕事回収は
、機械による漏れ間隙は別として、摺動弁及び回転子形
状によりねじ過給器の動作空間が吸入及び吐出側で完全
に閉鎖されかつ摺動弁がさらに、例えば引張装置の荷重
を除く際の完全な閉鎖又は絞り運転から圧縮運転への連
続的移行のような、絞り弁のすべての動作を引き受ける
場合にのみ、最適に達成され得る。The reserve of the throttle valve and the slide valve and the associated work recovery are such that, apart from the leakage gap caused by the machine, the operating space of the screw supercharger is completely closed on the suction and discharge sides due to the slide valve and rotor shape. and is only optimally achieved if the sliding valve also assumes all the movements of the throttle valve, such as complete closure when unloading the tension device or continuous transition from throttling to compression operation. obtain.
在来の制′ａ摺動弁では、特定の範囲における空気量の
調節は可能であるが、しかし動作空間の完全な連続的閉
鎖及び仕事回収は不可能である。With conventional control a sliding valves, it is possible to adjust the amount of air in a certain range, but complete continuous closure of the working space and work recovery are not possible.
引張装置６の荷重を除く際の摺動弁４の自動閉鎖は第７
図のｉ略図及び第１図の構造的構成に応じて１つ又は複
数のはね５により達成でき、これらのばねは、例えばボ
ーデンケーブルとして構成され得る引張袋＠６に抗して
動作する。The automatic closing of the sliding valve 4 when the load of the tension device 6 is removed is the seventh
Depending on the diagram of the figure and the structural configuration of FIG. 1, this can be achieved by one or more springs 5, which act against the tension bag @6, which can be configured, for example, as a Bowden cable.
はね装置の代わりに液圧復帰装置も第８図の概、略図に
応じて使用することができ、この場合、摺動弁の復帰は
、例えば摺動弁に入っている油の圧力上昇により行なわ
れる。Instead of a splash device, a hydraulic return device can also be used in accordance with the schematic representation in FIG. It is done.
摺動弁の駆動が第９図に応じて電動機１４及び例えば電
動機軸上の歯車１５及び摺動弁４上のラック１６を介し
て行なわれる場合は、例えば車両の加速ペダル位置に関
係して割部される電？ＩｊＪ機を介して摺動弁４が両方
向（開放又は閉鎖）に移動せしめられ得るならば、引張
装ｒａ６も省くことができる。If the sliding valve is actuated in accordance with FIG. 9 via an electric motor 14 and, for example, a gearwheel 15 on the motor shaft and a rack 16 on the sliding valve 4, then the distribution may occur, for example in relation to the position of the accelerator pedal of the vehicle. Parted electricity? If the sliding valve 4 can be moved in both directions (opening or closing) via the IJJ machine, the tensioning device RA6 can also be omitted.
例えば車両の加速ペダルを介して摺動弁４をできるだけ
容易に操作することができるようにするために、摺動弁
４の滑り面に滑りワニス又は摩擦係数を低下させる同じ
ような轡を設けることが必要になる。In order to be able to operate the sliding valve 4 as easily as possible, for example via the vehicle's accelerator pedal, the sliding surface of the sliding valve 4 can be provided with a sliding varnish or a similar lining that reduces the coefficient of friction. is required.
主回転子２と副回転子３との間のトルクは、−層短い構
造様式を得るために、同期化伝動装置９．１０又はねじ
過給器の回転子の断面範囲を介シテ伝達すレ博る。回転
子の断面範囲を介して動力を伝達する際は、摩耗を減ら
すために回転子を硬化又は被覆するのが有利である。The torque between the main rotor 2 and the auxiliary rotor 3 is transmitted through the synchronized transmission 9.10 or through the cross-sectional area of the rotor of a screw supercharger in order to obtain a shortened design. Expand. When transmitting power through the cross-sectional area of the rotor, it is advantageous to harden or coat the rotor in order to reduce wear.
第４図に概略的に示した内燃機関２０は、なるべくディ
ーゼル機関又は噴射式オツトー機関であるので、過給器
ｌは吸入空気しか圧縮しない。しかし、本発明により構
成されたねじ圧縮機を過給器として気化器付き機関にお
いても、このねじ圧縮機が気化器から送られる混合気を
前圧縮するように、使用することも可能である。The internal combustion engine 20 shown diagrammatically in FIG. 4 is preferably a diesel engine or an injection engine, so that the supercharger l only compresses intake air. However, it is also possible to use the screw compressor constructed according to the present invention as a supercharger in an engine equipped with a carburetor so that the screw compressor precompresses the air-fuel mixture sent from the carburetor.
第４図に示した好ましい実施例では、過給器ｌは機関２
０のクランク軸により変速機２２を介して永続的に駆動
される。しかし過給器を必要のある場合にのみ連結及び
切り離し可能な変速機を介して接続することも可能であ
る。In the preferred embodiment shown in FIG.
It is permanently driven via the transmission 22 by the 0 crankshaft. However, it is also possible to connect the supercharger via a transmission that can be connected and disconnected only when necessary.
第１図は本発明の実施例による、摺動弁で制御されるね
じ圧縮機の縦断面図、第２図は第１図のＡ−Ａ線に沿う
断面図、第３図は第１図のＢ−Ｂ線に沿う断面図、第４
図は第１図ないし第３図によるねじ圧縮機を過給器とし
て備えた内燃機関の概略構成図、第５図はねじ回転子の
角度位置に対する隔室容積の依存関係を示す線図、第６
図はねじ回転子機械の圧力−容積状態の線図、第７図、
第８区及び第９図は摺動弁の構造を変えたねじ回転子機
械の第１図と同じような概略断面図である。
ｌ・・・ねじ回転子機械、４・・・摺動弁、２０・・・
内燃機関、２１・・・加速ペダルベシュレンクテルｅハ
フトウング
第３図
第４区
第５図
り甲
第６図
第７図
工
第８図
第９図
土
１つ ＩＱFIG. 1 is a longitudinal sectional view of a screw compressor controlled by a sliding valve according to an embodiment of the present invention, FIG. 2 is a sectional view taken along line A-A in FIG. 1, and FIG. Sectional view along line B-B of 4th
The figures are a schematic diagram of an internal combustion engine equipped with the screw compressor shown in Figures 1 to 3 as a supercharger, Figure 5 is a diagram showing the dependence of compartment volume on the angular position of the screw rotor, and Figure 5 is a diagram showing the dependence of compartment volume on the angular position of the screw rotor. 6
The figure is a diagram of the pressure-volume state of a screw rotor machine, Fig. 7,
Sections 8 and 9 are schematic sectional views similar to FIG. 1 of a screw rotor machine with a different structure of the sliding valve. l...screw rotor machine, 4...sliding valve, 20...
Internal combustion engine, 21... Accelerator pedal Beschlenktel e Haftung Figure 3 Section 4 Section 5 Figure A Figure 6 Figure 7 Engineering Figure 8 Figure 9 1 piece IQ
Claims (1)
いて、圧縮機がねじ回転子機械（１）として構成されか
つ吸入側に摺動弁（４）を持ち、この摺動弁によりねじ
回転子機械の吸入断面が完全に閉鎖可能であり又は調整
されて開放可能であり、摺動弁（４）が、機関（２０）
の吸入量を制御する絞り機構でありかつ加速ペダル（２
１）などにより機関（２０）の出力制御部材が操作可能
であることを特徴とする過給内燃機関。 ２ ねじひれとねじ溝が互いにかみ合う少なくとも２つ
のねじ回転子が、互いに貫通する、軸線に対して平行な
シリンダ孔により形成されかつ端壁により区画されたハ
ウジングの動作空間内に配置され、このハウジングが、
動作空間へ開口している低圧接続管片と高圧接続管片及
び回転子軸線に対して平行に移動可能に設けられた摺動
弁を持ち、この摺動弁が、低圧接続管片に対応する側に
動作空間の周壁の一部を形成しかつ摺動弁の位置に応じ
て低圧接続管片から動作空間内への流れ通路を多かれ少
なかれ開放する、摺動弁で制御されるねじ回転子機械に
おいて、低圧接続管片（７）と動作空間との接続部が摺
動弁（４）により完全に閉鎖可能であることを特徴とす
る、請求項１に記載の内燃機関に特に過給器として使用
される、摺動弁で制御されるねじ回転子機械。 ３ 摺動弁（４）が、閉鎖方向に見て前方に位置する端
面に、摺動弁開口の範囲にある、互いにかみ合う回転子
歯の歯先線の経過に一致する輪郭（４ａ）を持ち、摺動
弁（４）が低圧側の端壁（１２）にある凹所を通つてこ
の端壁を越えて移動可能であり、摺動弁輪郭の三角形に
より形成された開口が低圧接続管片（７）と動作空間と
の間で閉鎖されていることを特徴とする、請求項２に記
載のねじ回転子機械。 ４ 両方の回転子（２、３）のねじひれ及びねじ溝がそ
れぞれ、同じに構成された前及び後歯面を持つ対称断面
形状を持つていることを特徴とする、請求項２に記載の
ねじ回転子機械。 ５ 摺動弁（４）が復帰装置（５）により閉鎖位置に保
持されかつ操作装置（６）により復帰力に抗して開放方
向に移動可能であることを特徴とする、請求項２に記載
のねじ回転子機械。[Claims] 1. A supercharged internal combustion engine having a compressor disposed in the suction passage, in which the compressor is configured as a screw rotor machine (1) and has a sliding valve (4) on the suction side. By means of the sliding valve the suction section of the screw rotor machine can be completely closed or can be opened in a controlled manner, the sliding valve (4)
It is a throttle mechanism that controls the intake amount of
1) A supercharged internal combustion engine characterized in that an output control member of the engine (20) is operable. 2. At least two screw rotors whose screw fins and screw grooves engage with each other are arranged in a working space of a housing defined by mutually penetrating cylinder holes parallel to the axis and defined by end walls, and the housing but,
It has a low-pressure connecting piece and a high-pressure connecting piece that open to the operating space, and a sliding valve that is movable in parallel to the rotor axis, and this sliding valve corresponds to the low-pressure connecting piece. A screw rotor machine controlled by a sliding valve which forms part of the circumferential wall of the working space on the side and which, depending on the position of the sliding valve, opens more or less a flow path from the low-pressure connecting piece into the working space. 2. An internal combustion engine according to claim 1, in particular as a supercharger, characterized in that the connection between the low-pressure connecting piece (7) and the working space is completely closable by means of a sliding valve (4). Used in screw rotor machines controlled by sliding valves. 3. The sliding valve (4) has, on its end face located forward in the closing direction, a contour (4a) that corresponds to the course of the tip lines of the mutually meshing rotor teeth in the area of the sliding valve opening. , the sliding valve (4) is movable through a recess in the end wall (12) on the low-pressure side and beyond this end wall, the opening formed by the triangle of the sliding valve profile being connected to the low-pressure connecting piece. Screw rotor machine according to claim 2, characterized in that it is closed between (7) and the working space. 4. The rotor according to claim 2, characterized in that the thread fins and thread grooves of both rotors (2, 3) each have a symmetrical cross-sectional shape with identically configured front and rear tooth flanks. Screw rotor machine. 5. according to claim 2, characterized in that the sliding valve (4) is held in the closed position by a return device (5) and is movable in the opening direction against a return force by an actuating device (6) screw rotor machine.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3803044A DE3803044A1 (en) | 1988-02-02 | 1988-02-02 | SLIDER-CONTROLLED SCREW-ROTOR MACHINE AND CHARGED COMBUSTION ENGINE |
| DE3803044.6 | 1988-02-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01310119A true JPH01310119A (en) | 1989-12-14 |
| JPH0654092B2 JPH0654092B2 (en) | 1994-07-20 |
Family
ID=6346453
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1019926A Expired - Fee Related JPH0654092B2 (en) | 1988-02-02 | 1989-01-31 | Supercharged internal combustion engine |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0326663B1 (en) |
| JP (1) | JPH0654092B2 (en) |
| KR (1) | KR930005961B1 (en) |
| DE (2) | DE3803044A1 (en) |
| ES (1) | ES2035220T3 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005066503A1 (en) * | 2004-01-08 | 2005-07-21 | Koichi Hatamura | Positive displacement compressor and supercharger using the same |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2524257B2 (en) * | 1990-11-06 | 1996-08-14 | 本田技研工業株式会社 | Supercharging pressure control method in internal combustion engine |
| JPH0669993U (en) * | 1993-03-09 | 1994-09-30 | 清 秋生 | Toy whistle |
| SE501252C2 (en) * | 1993-04-21 | 1994-12-19 | Opcon Autorotor Ab | Supercharged internal combustion engine |
| GB9912645D0 (en) * | 1999-05-28 | 1999-07-28 | Seneca Tech Ltd | Super-charger for i.c. engine |
| US8539769B2 (en) * | 2009-10-14 | 2013-09-24 | Craig N. Hansen | Internal combustion engine and supercharger |
| US8813492B2 (en) * | 2009-10-14 | 2014-08-26 | Hansen Engine Corporation | Internal combustion engine and supercharger |
| DE102015007552A1 (en) | 2015-06-16 | 2016-12-22 | Man Diesel & Turbo Se | Screw machine and method of operating the same |
| DE102021134652B3 (en) | 2021-12-23 | 2023-05-11 | Man Energy Solutions Se | screw compressor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1293384B (en) * | 1959-06-04 | 1969-04-24 | Svenska Rotor Maskiner Ab | Device for controlling a screw rotor machine |
| WO1987002417A1 (en) * | 1985-10-14 | 1987-04-23 | Svenska Rotor Maskiner Ab | An arrangement in an internal combustion engine provided with a supercharger |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1258650A (en) * | 1960-06-01 | 1961-04-14 | Svenska Rotor Maskiner Ab | Axial displacement sliders for helical rotor machines |
| DE8415188U1 (en) * | 1984-05-18 | 1985-08-22 | Pierburg Gmbh & Co Kg, 4040 Neuss | Device for controlling the inlet opening of a rotary vane or vane compressor |
-
1988
- 1988-02-02 DE DE3803044A patent/DE3803044A1/en not_active Withdrawn
- 1988-11-10 ES ES198888118719T patent/ES2035220T3/en not_active Expired - Lifetime
- 1988-11-10 DE DE8888118719T patent/DE3875471D1/en not_active Expired - Lifetime
- 1988-11-10 EP EP88118719A patent/EP0326663B1/en not_active Expired - Lifetime
-
1989
- 1989-01-14 KR KR1019890000384A patent/KR930005961B1/en not_active IP Right Cessation
- 1989-01-31 JP JP1019926A patent/JPH0654092B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1293384B (en) * | 1959-06-04 | 1969-04-24 | Svenska Rotor Maskiner Ab | Device for controlling a screw rotor machine |
| WO1987002417A1 (en) * | 1985-10-14 | 1987-04-23 | Svenska Rotor Maskiner Ab | An arrangement in an internal combustion engine provided with a supercharger |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005066503A1 (en) * | 2004-01-08 | 2005-07-21 | Koichi Hatamura | Positive displacement compressor and supercharger using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| DE3875471D1 (en) | 1992-11-26 |
| ES2035220T3 (en) | 1993-04-16 |
| JPH0654092B2 (en) | 1994-07-20 |
| EP0326663B1 (en) | 1992-10-21 |
| KR930005961B1 (en) | 1993-06-30 |
| EP0326663A3 (en) | 1990-03-14 |
| DE3803044A1 (en) | 1989-08-10 |
| KR890013321A (en) | 1989-09-22 |
| EP0326663A2 (en) | 1989-08-09 |
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| LAPS | Cancellation because of no payment of annual fees |