EP0156962B1 - Expansion valve - Google Patents

Expansion valve Download PDF

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Publication number
EP0156962B1
EP0156962B1 EP84113580A EP84113580A EP0156962B1 EP 0156962 B1 EP0156962 B1 EP 0156962B1 EP 84113580 A EP84113580 A EP 84113580A EP 84113580 A EP84113580 A EP 84113580A EP 0156962 B1 EP0156962 B1 EP 0156962B1
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EP
European Patent Office
Prior art keywords
tappet
valve
diaphragm
plunger
valve according
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
Application number
EP84113580A
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German (de)
French (fr)
Other versions
EP0156962A1 (en
Inventor
Rudibert Dipl.-Ing. Götzenberger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ernst Flitsch GmbH and Co
Original Assignee
Ernst Flitsch GmbH and Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ernst Flitsch GmbH and Co filed Critical Ernst Flitsch GmbH and Co
Publication of EP0156962A1 publication Critical patent/EP0156962A1/en
Application granted granted Critical
Publication of EP0156962B1 publication Critical patent/EP0156962B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms

Definitions

  • the invention relates to a valve with the features specified in the preamble of claim 1, which for installation in a compressor consisting of a compressor, condenser and evaporator. medium circulation is determined.
  • a valve which has the aforementioned construction is known from DE-C-976 465. With this valve, the movement of which is caused by the pressure of the flow medium and which is used, for example, in washing machines, short closing times are to be achieved and the occurrence of water hammer is to be prevented.
  • This valve is not suitable for metering the liquid refrigerant injected into an evaporator of a refrigerant circuit or for solving the problems on which the invention is based.
  • thermostatic expansion valves are usually used, such as those used for.
  • B. DE-A-2 932 906 shows that are controlled by means of a temperature sensor attached to the evaporator outlet and containing a vapor-forming liquid in such a way that the vapor pressure of the filling medium of the temperature sensor acts on the control head of the expansion valve, the desired being achieved by means of an overheating spring Overheating is set at the evaporator outlet.
  • thermostatic expansion valves have some disadvantages. Since the valves have to be adapted to the refrigerant used in each case, this necessitates the provision of a corresponding number of functionally similar devices or the provision of devices with exchangeable nozzles of different sizes. In addition, with such valves the time constant, which is dependent on the dimensions of the diaphragm or corrugated tube diameter, the spring hardness of the overheating spring, the selected nozzle size and the filling medium of the control system, can no longer be changed in a finished valve.
  • the invention has for its object to provide an expansion valve of the aforementioned type, which does not have the disadvantages mentioned, does not require a capillary tube for connecting the temperature sensor to the control head of the valve and enables remote monitoring of the functional sequence during operation.
  • valve according to the invention both the smallest and the greatest outputs can be controlled properly, regardless of the refrigerant used, gas-filled components which are exposed to the risk of leakage are eliminated, and the interchangeability of the electrical parts ensures a longer service life.
  • the valve body 1 has an inlet 2 for the refrigerant which receives the suction line and an outlet 3 to which the line leading to the evaporator is connected.
  • a sleeve 4 forming the valve seat 41, through which the valve tappet 5 is guided.
  • the cooperating with the valve seat 41 is formed by a plastic washer 6 which comprises the valve tappet 5 and on the one hand rests against an annular shoulder formed on the valve tappet and on the other hand against an O-ring which is arranged in a recess in an annular body 7 whose shoulder the ring flange of a sleeve 9 receiving a filter and against whose ring flange a coil spring 8 rests, which is supported on an abutment ring 10 which can be moved in the longitudinal direction of the valve by means of an Allen screw 11 engaging in a thread cut into the valve body 1 .
  • the plunger 5 has a capillary bore 51 and at its upper end an annular shoulder 52 which bears against the membrane 12 and a pin-shaped end 53 which extends through an axial recess in the membrane 12 and has a reduced diameter and which has the end face of a plunger movable in the longitudinal direction of the valve 14 is opposite.
  • the end face of the annular shoulder 52 of the plunger 5 has a recess, from which notches or openings 54 penetrating the casing of the plunger 5 extend, which open into a channel 31 leading to the outlet 3.
  • the plunger is tapered in order to achieve a tension-proportional stroke of the plunger.
  • a retaining spring 21 against the upper end face of the plunger, the abutment of which is formed by a screw bolt 18 rigidly connected to the guide sleeve 15, onto which a crown nut 19 is screwed between the annular end face and the upper end plate of the housing 17 accommodating the magnet coil 16, a sealing ring 20 is arranged.
  • FIG. 1 Embodiment modified in such a way that the flow direction of the refrigerant is reversed and the refrigerant flows from the area 3 through a radial bore provided in the plunger 5 directly into the capillary bore 51 of the plunger 5.
  • the capillary bore 51 is closed at the lower end of the plunger 5, and the arrangement of the filter 9 can be dispensed with.
  • a screen acting as a filter can be inserted into the capillary bore 51.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Magnetically Actuated Valves (AREA)

Description

Die Erfindung betrifft ein Ventil mit den im Oberbegriff des Anspruchs 1 angegebenen Merkmalen, das zum Einbau in einen aus Kompressor, Kondensator und Verdampfer bestehenden Kälte- . mittelkreislauf bestimmt ist.The invention relates to a valve with the features specified in the preamble of claim 1, which for installation in a compressor consisting of a compressor, condenser and evaporator. medium circulation is determined.

Ein Ventil, das den vorgenannten konstruktiven Aufbau aufweist, ist aus der DE-C-976 465 bekannt. Mit diesem Ventil, dessen Bewegung durch den Druck des Durchflußmediums bewirkt wird und das beispielsweise bei Waschmaschinen verwendet wird, sollen kurze Schließzeiten erreicht und das Auftreten von Wasserschlägen ausgeschlossen werden. Zur Dosierung des in einen Verdampfer eines Kältemittelkreislaufes eingespritzten flüssigen Kältemittels sowie zur Lösung der der Erfindung zugrundeliegenden Aufgaben ist dieses Ventil nicht geeignet.A valve which has the aforementioned construction is known from DE-C-976 465. With this valve, the movement of which is caused by the pressure of the flow medium and which is used, for example, in washing machines, short closing times are to be achieved and the occurrence of water hammer is to be prevented. This valve is not suitable for metering the liquid refrigerant injected into an evaporator of a refrigerant circuit or for solving the problems on which the invention is based.

Zur Dosierung des in einen Verdampfer eingespritzten flüssigen Kältemittels werden meist thermostatische Expansionsventile eingesetzt, wie sie z. B. die DE-A-2 932 906 zeigt, die mittels eines am Verdampferausgang angebrachten, eine dampfbildende Flüssigkeit enthaltenden Temperaturfühlers in der Weise gesteuert werden, daß der Dampfdruck des Füllmediums des Temperaturfühlers auf den Steuerkopf des Expansionsventils wirkt, wobei mittels einer Überhitzungsfeder die gewünschte Überhitzung am Verdampferausgang eingestellt wird.For metering the liquid refrigerant injected into an evaporator, thermostatic expansion valves are usually used, such as those used for. B. DE-A-2 932 906 shows that are controlled by means of a temperature sensor attached to the evaporator outlet and containing a vapor-forming liquid in such a way that the vapor pressure of the filling medium of the temperature sensor acts on the control head of the expansion valve, the desired being achieved by means of an overheating spring Overheating is set at the evaporator outlet.

Diese thermostatischen Expansionsventile weisen jedoch einige Nachteile auf. Da die Ventile dem jeweils verwendeten Kältemittel angepasst sein müssen, macht dies die Bereitstellung einer entsprechenden Vielzahl funktionell gleichartiger Geräte bzw. die Bereitstellung von Geräten mit auswechselbaren Düsen unterschiedlicher Größe notwendig. Außerdem kann bei solchen Ventilen die Zeitkonstante, die von den Abmessungen des Membran- oder Wellrohrdurchmessers, der Federhärte der Überhitzungsfeder, der gewählten Düsengröße und dem Füllmedium des Steuersystems abhängig ist, bei einem fertigen Ventil nicht mehr geändert werden.However, these thermostatic expansion valves have some disadvantages. Since the valves have to be adapted to the refrigerant used in each case, this necessitates the provision of a corresponding number of functionally similar devices or the provision of devices with exchangeable nozzles of different sizes. In addition, with such valves the time constant, which is dependent on the dimensions of the diaphragm or corrugated tube diameter, the spring hardness of the overheating spring, the selected nozzle size and the filling medium of the control system, can no longer be changed in a finished valve.

Der Erfindung liegt die Aufgabe zugrunde, ein Expansionsventil der vorgenannten Gattung zu schaffen, das die erwähnten Nachteile nicht aufweist, kein Kapillarrohr zur Verbindung des Temperaturfühlers mit dem Steuerkopf des Ventils benötigt und eine Fernüberwachung des Funktionsablaufs während des Betriebs ermöglicht.The invention has for its object to provide an expansion valve of the aforementioned type, which does not have the disadvantages mentioned, does not require a capillary tube for connecting the temperature sensor to the control head of the valve and enables remote monitoring of the functional sequence during operation.

Diese Aufgabe wird gemäß der Erfindung mit den im Kennzeichen des Anspruchs 1 angegebenen Mitteln gelöst. Vorteilhafte Ausgestaltungen des erfindungsgemäßen Ventils sind aus den Unteransprüchen ersichtlich.This object is achieved according to the invention with the means specified in the characterizing part of claim 1. Advantageous embodiments of the valve according to the invention can be seen from the subclaims.

Mit dem erfindungsgemäßen Ventil können sowohl kleinste als auch größte Leistungen einwandfrei unabhängig vom jeweils verwendeten Kältemittel ausgesteuert werden, gasgefüllte, der Gefahr der Undichtigkeit ausgesetzte Bauteile entfallen, und die Austauschbarkeit der elektrischer Teile gewährleistet eine größere Lebensdauer.With the valve according to the invention, both the smallest and the greatest outputs can be controlled properly, regardless of the refrigerant used, gas-filled components which are exposed to the risk of leakage are eliminated, and the interchangeability of the electrical parts ensures a longer service life.

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Expansionsventils in schematischer Weise dargestellt. Es zeigen :

  • Fig. 1 einen Längsschnitt durch das Ventil ;
  • Fig. 2 einen Ausschnitt der Fig. 1 in vergrößertem Maßstab.
In the drawing, an embodiment of the expansion valve according to the invention is shown in a schematic manner. Show it :
  • 1 shows a longitudinal section through the valve.
  • Fig. 2 shows a detail of Fig. 1 on an enlarged scale.

Der Ventilkörper 1 weist einen die Saugleitung aufnehmenden Einlaß 2 für das Kältemittel und einen Auslaß 3 auf, an den die zum Verdampfer führende Leitung angeschlossen ist. Im Ventilkörper ist eine den Ventilsitz 41 bildende Hülse 4 angeordnet, durch die der Ventilstößel 5 hindurchgeführt ist. Der mit dem Ventilsitz 41 zusammenwirkende Schließkörper wird durch eine aus Kunststoff bestehende Ringscheibe 6 gebildet, die den Ventilstößel 5 umfaßt und einerseits gegen eine am Ventilstößel gebildete Ringschulter und andererseits gegen einen O-Ring anliegt, der in einer Aussparung eines Ringkörpers 7 angeordnet ist, gegen dessen Schulter der Ringflansch einer einen Filter 9 aufnehmenden Hülse und gegen deren Ringflansch eine Schraubenfeder 8 anliegt, die sich an einem Widerlagerring 10 abstützt, der in Längsrichtung des Ventils mittels einer in ein in den Ventilkörper 1 eingeschnittenes Gewinde eingreifenden Inbus-Schraube 11 verschoben werden kann.The valve body 1 has an inlet 2 for the refrigerant which receives the suction line and an outlet 3 to which the line leading to the evaporator is connected. Arranged in the valve body is a sleeve 4 forming the valve seat 41, through which the valve tappet 5 is guided. The cooperating with the valve seat 41 is formed by a plastic washer 6 which comprises the valve tappet 5 and on the one hand rests against an annular shoulder formed on the valve tappet and on the other hand against an O-ring which is arranged in a recess in an annular body 7 whose shoulder the ring flange of a sleeve 9 receiving a filter and against whose ring flange a coil spring 8 rests, which is supported on an abutment ring 10 which can be moved in the longitudinal direction of the valve by means of an Allen screw 11 engaging in a thread cut into the valve body 1 .

Der Stößel 5 weist eine Kapillarbohrung 51 und an seinem oberen Ende eine gegen die Membran 12 anliegende Ringschulter 52 und ein durch eine axiale Aussparung der Membran 12 hindurchgreifendes, einen verringerten Durchmesser aufweisendes zapfenförmiges Ende 53 auf, dem die Stirnfläche eines in Längsrichtung des Ventils beweglichen Plungers 14 gegenüberliegt. Die Stirnfläche der Ringschulter 52 des Stößels 5 weist eine Vertiefung auf, von der den Mantel des Stößels 5 durchsetzende Kerben oder Durchbrüche 54 ausgehen, die in einen zum Auslaß 3 führenden Kanal 31 münden. Zwischen dem Ende 53 und der Membran 12 besteht ein Ringspalt 13, so daß bei von dem Stößel 5 abgehobenem Plunger 14 in den Raum oberhalb der Membran eingespritztes und in diesem Raum verdampfendes Kältemittel durch den Ringspalt 13 in die Verdampferleitung gelangen kann. Hierbei übt das oberhalb der Membran verdampfte Kältemittel auf die Membran einen Druck aus, der den auf der Unterseite der Membran herrschenden Verdampferdruck übersteigt. Um einen dichten Abschluß zu gewährleisten, ist an der unteren Stirnfläche des Plungers 14 eine Dichtscheibe 22 aus nachgiebigem Werkstoff angeordnet. Der Plunger 14 gleitet in einer Führungshülse 15 aus unmagnetischem Material, so daß die Kraftlinien der um die Führungshülse 15 angeordneten Magnetspule in den Plunger eintreten können. An seinem oberen Ende ist der Plunger konisch verjüngt, um auf diese Weise einen spannungsproportionalen Hub des Plungers zu erzielen. Um einen Einbau des Expansionsventils in jeder Lage zu ermöglichen, beispielsweise das Expansionsventil auch in Fahrzeuge einbauen zu können, in denen es Fliehkräften unterworfen ist, liegt gegen die obere Stirnfläche des Plungers eine Haltefeder 21 an, deren Widerlager durch einen starr mit der Führungshülse 15 verbundenen Schraubenbolzen 18 gebildet wird, auf den eine Kronenmutter 19 aufgeschraubt ist, zwischen deren ringförmiger Stirnfläche und der oberen Abschlußplatte des die Magnetspule 16 aufnehmenden Gehäuses 17 ein Dichtring 20 angeordnet ist.The plunger 5 has a capillary bore 51 and at its upper end an annular shoulder 52 which bears against the membrane 12 and a pin-shaped end 53 which extends through an axial recess in the membrane 12 and has a reduced diameter and which has the end face of a plunger movable in the longitudinal direction of the valve 14 is opposite. The end face of the annular shoulder 52 of the plunger 5 has a recess, from which notches or openings 54 penetrating the casing of the plunger 5 extend, which open into a channel 31 leading to the outlet 3. Between the end 53 and the membrane 12 there is an annular gap 13, so that when the plunger 14 is lifted from the plunger 5, refrigerant injected into the space above the membrane and evaporating in this space can pass through the annular gap 13 into the evaporator line. In this case, the refrigerant evaporated above the membrane exerts a pressure on the membrane that exceeds the evaporator pressure prevailing on the underside of the membrane. In order to ensure a tight seal, a sealing washer 22 made of flexible material is arranged on the lower end face of the plunger 14. The plunger 14 slides in a guide sleeve 15 made of non-magnetic material, so that the lines of force of the magnet coil arranged around the guide sleeve 15 can enter the plunger. At its upper end, the plunger is tapered in order to achieve a tension-proportional stroke of the plunger. To enable the expansion valve to be installed in any position, For example, to be able to install the expansion valve in vehicles in which it is subjected to centrifugal forces, there is a retaining spring 21 against the upper end face of the plunger, the abutment of which is formed by a screw bolt 18 rigidly connected to the guide sleeve 15, onto which a crown nut 19 is screwed between the annular end face and the upper end plate of the housing 17 accommodating the magnet coil 16, a sealing ring 20 is arranged.

Sollte bei dem in Fig. 1 dargestellten Strömungsverlauf des Kältemittels im Bereich des Ventilsitzes 41 und der das Ventil schließenden, einen Flachsitz bildenden Ringscheibe 6 ein Abriß der Strömung befürchtet werden, der zu Schwingungen des Ventilstößels 5 führt, so kann das in Fig. 1 dargestellte Ausführungsbeispiel in der Weise abgewandelt werden, daß die Strömungsrichtung des Kältemittels umgekehrt wird und das Kältemittel aus dem Bereich 3 durch eine in dem Stößel 5 vorgesehene Radialbohrung unmittelbar in die Kapillarbohrung 51 des Stößels 5 einfließt. Im diesem Fall ist die Kapillarbohrung 51 am unteren Ende des Stößels 5 verschlossen, und auf die Anordnung des Filters 9 kann verzichtet werden. Anstelle des Filters 9 kann in die Kapillarbohrung 51 ein als Filter wirkendes Siebeingesetzt werden.If, in the flow profile of the refrigerant in the region of the valve seat 41 and the ring disk 6 closing the valve and forming a flat seat shown in FIG. 1, there is a fear that the flow may be interrupted, which leads to vibrations of the valve tappet 5, this can be shown in FIG. 1 Embodiment modified in such a way that the flow direction of the refrigerant is reversed and the refrigerant flows from the area 3 through a radial bore provided in the plunger 5 directly into the capillary bore 51 of the plunger 5. In this case, the capillary bore 51 is closed at the lower end of the plunger 5, and the arrangement of the filter 9 can be dispensed with. Instead of the filter 9, a screen acting as a filter can be inserted into the capillary bore 51.

Claims (7)

1. Valve comprising a tappet (5) which is hydro- pneumatically controlled by a diaphragm (12), exhibits an axial capillary bore (51), in an axial cut-out penetrates the diaphragm (12) with its smaller diameter end (53) opposite to the valve face (41), and bears with one shoulder (52) against the diaphragm (12); and comprising a plunger (14) operating on the tappet (5) and arranged inside a magnetic coil (16) excitable by a transducer, said plunger effecting the closing and opening of the capillary tube (51), characterised in that the valve is constructed as an expansion valve for injecting a coolant into the evaporator of a refrigeration unit, that between the tappet end (53) and the diaphragm (12) is an annular gap (13) and that the end surface forming the shoulder (52) of the tappet (5) exhibits a depression which via the annular gap (13) formed by the axial cut-out in the diaphragm (12) communicates with the control chamber lying above the diaphragm (12) and via openings (54) in the tappet (5) and a passage (31) communicates with the line leading to the evaporator.
2. Valve according to Claim 1, characterised in that the end of the plunger (14) opposite to the diaphragm (12) is conically tapered.
3. Valve according to Claim 1 or 2, characterised in that on the end side of the housing (17) enclosing the magnetic coil (16) there is arranged a spring (21) which exerts a pressure on the plunger (14).
4. Valve according to one of Claims 1 to 3, characterised in that in the valve body (1) which exhibits an inlet (2) and an outlet (3) for the coolant there is arranged a spring (8) which exerts a pressure on the tappet (5).
5. Valve according to one of claims 1 to 4, characterised in that the valve face (41) is formed by the end surface of a sleeve (4) penetrated by the tappet (5) and a closing member co-operating with the valve face is formed by a ring washer (6) made of plastic and bearing against an annular shoulder of the tappet (5).
6. Valve according to one of Claims 1 to 5, characterised in that before the lower opening of the capillary bore (51) of the tappet (5) there is arranged a filter (9) surrounded by a sleeve.
7. Valve according to one of Claims 1 to 6, characterised in that on the end surface of the plunger (14) opposite to the tappet end (53) penetrating the diaphragm (12) there is arranged a washer (22) of pliable material.
EP84113580A 1983-12-12 1984-11-10 Expansion valve Expired EP0156962B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3344816 1983-12-12
DE19833344816 DE3344816A1 (en) 1983-12-12 1983-12-12 EXPANSION VALVE

Publications (2)

Publication Number Publication Date
EP0156962A1 EP0156962A1 (en) 1985-10-09
EP0156962B1 true EP0156962B1 (en) 1988-03-23

Family

ID=6216673

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84113580A Expired EP0156962B1 (en) 1983-12-12 1984-11-10 Expansion valve

Country Status (7)

Country Link
US (1) US4606199A (en)
EP (1) EP0156962B1 (en)
JP (1) JPS60140074A (en)
BR (1) BR8406334A (en)
DE (2) DE3344816A1 (en)
DK (1) DK591184A (en)
ES (1) ES283335Y (en)

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US4852364A (en) * 1987-10-23 1989-08-01 Sporlan Valve Company Expansion and check valve combination
BR8804215A (en) * 1988-08-12 1990-03-27 Brasil Compressores Sa BLOCKING VALVE FOR COOLING OR AIR CONDITIONING SYSTEMS
DE3829101A1 (en) * 1988-08-27 1990-03-01 Sueddeutsche Kuehler Behr THERMOSTATIC EXPANSION VALVE
US4928494A (en) * 1988-12-20 1990-05-29 American Standard Inc. Incremental electrically actuated valve
DE3922591A1 (en) * 1989-07-10 1991-01-24 Danfoss As SERVO CONTROLLED EXPANSION VALVE FOR AN EASILY VAPORABLE FLUID
US4986085A (en) * 1989-09-12 1991-01-22 American Standard Inc. Incremental electrically actuated valve
EP0689015A1 (en) * 1994-06-21 1995-12-27 Staefa Control System Scs Ag Control valve with actuating drive
US6418741B1 (en) 2000-05-03 2002-07-16 Parker Hannifin Corporation Expansion/check valve assembly including a reverse flow rate adjustment device
CN101988587A (en) * 2009-08-06 2011-03-23 北京菁华昱创节能设备有限公司 Multifunctional control valve
US20150052924A1 (en) * 2013-08-22 2015-02-26 Standard Motor Products, Inc. Thermal Expansion Valve with Power Element
CN104482274B (en) * 2014-10-28 2016-09-14 珠海格力电器股份有限公司 Electronic expansion valve
US10993546B2 (en) * 2016-10-28 2021-05-04 Sleep Number Corporation Noise reducing plunger
US11832728B2 (en) 2021-08-24 2023-12-05 Sleep Number Corporation Controlling vibration transmission within inflation assemblies

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DE2632331A1 (en) * 1975-07-25 1977-02-17 Midland Ross Corp INDEPENDENT ADJUSTMENT DEVICE FOR BRAKES
US3997035A (en) * 1975-09-02 1976-12-14 Borg-Warner Corporation Automatic slack adjuster for vehicle brakes
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GB2087012A (en) * 1980-07-21 1982-05-19 Kelsey Hayes Co Slack adjuster

Also Published As

Publication number Publication date
ES283335Y (en) 1986-01-01
DK591184D0 (en) 1984-12-11
JPS60140074A (en) 1985-07-24
US4606199A (en) 1986-08-19
BR8406334A (en) 1985-10-08
ES283335U (en) 1985-05-16
DE3344816A1 (en) 1985-06-20
DK591184A (en) 1985-06-13
EP0156962A1 (en) 1985-10-09
DE3470094D1 (en) 1988-04-28

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