DE10023455C2 - Pressure valve for a compressor - Google Patents

Pressure valve for a compressor

Info

Publication number
DE10023455C2
DE10023455C2 DE2000123455 DE10023455A DE10023455C2 DE 10023455 C2 DE10023455 C2 DE 10023455C2 DE 2000123455 DE2000123455 DE 2000123455 DE 10023455 A DE10023455 A DE 10023455A DE 10023455 C2 DE10023455 C2 DE 10023455C2
Authority
DE
Germany
Prior art keywords
catch plate
part
leaf spring
valve
plate
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 - Fee Related
Application number
DE2000123455
Other languages
German (de)
Other versions
DE10023455A1 (en
Inventor
Jan Thomsen
Frank Holm Iversen
Preben Bjerre
Morten Svendsen
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.)
Secop GmbH
Original Assignee
Secop GmbH
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
Priority to DE19923732 priority Critical
Application filed by Secop GmbH filed Critical Secop GmbH
Priority to DE2000123455 priority patent/DE10023455C2/en
Publication of DE10023455A1 publication Critical patent/DE10023455A1/en
Application granted granted Critical
Publication of DE10023455C2 publication Critical patent/DE10023455C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10Adaptations or arrangements of distribution members
    • F04B39/1073Adaptations or arrangements of distribution members the members being reed valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027Pulsation and noise damping means

Abstract

A pressure valve for a compressor, which has at least one piston-cylinder unit, the cylinder of which is closed by a valve plate with at least one valve opening, has a leaf spring (13) as the valve closure part, the opening movement of which is limited by a catch plate (1). Leaf spring (13) and catch plate (1) are clamped on one side on the valve plate. The catch plate (1) has a clamping part (2) and a contact part (3) bent away from the valve opening and at least one stiffening element (6, 7) between its clamping part (2) and the valve opening in order to place the natural vibration frequency of the catching plate outside the listening area, So that vibrations of the catch plate that occur as a result of the back and forth movement of the leaf spring when closing and opening the pressure valve are as inaudible as possible, it is ensured that the catch plate (1) is curved away from the valve opening and each stiffening element (6, 7) around one forms the same amount downward over the clamping part (2) of the catch plate (1) protruding projection of the catch plate (1).

Description

The invention relates to a pressure valve for egg NEN compressor, especially a hermetic capsule th compressor, which has at least one piston-cylinder Has unit, the cylinder through a Ventilplat completed with at least one valve opening is, the valve opening by a leaf spring as Valve closure part is covered, the opening movement is limited by a catch plate, with Blattfe the and catch plate on one side of the valve plate are clamped and the catch plate is a clamping part system part bent away from the valve opening and between minimum of their clamping part and the valve opening least has a stiffening element.

Such a valve is from DE 24 51 207 A1 known. There the catch plate (also "valve catcher" ge called) an extending over the entire length Stiffening element in the form of a bead or rib, de ridge with the underside facing the leaf spring of the clamping part of the catch plate is aligned. The catch plate  and the leaf spring are about sickle or hoofed Sen-shaped and clamped at both ends. The Flexural strength of the catch plate is therefore due to the Flexural rigidity of her legs determined. Beyond that the catch plate is angled out. The angled Sections are straight forward. If the leaf spring from that Valve seat is moved away, it pushes the angled part of the contact part of the catch plate, which can lead to vibrations of the catch plate.

Another valve is from the European patent Document EP 0 699 837 B1 known, in which the plant part is curved away from the valve opening. The width of the Leaf spring is at its free, the valve opening off covering end larger than at its clamped end. The catch plate has in her away from the valve plate curved part two sections with constant curvature mung radius. This configuration is desirable dimensions increasing towards the free end of the leaf spring Stiffness of the leaf spring with increasing deflection, but also a large moving mass and an un desired flow resistance in the wider range of Leaf spring opposite the valve opening.

A similar valve is known from EP 0 774 582 A1 knows, in which the contact surface of the catch plate one straight section parallel to the valve plate and one section curved away from the valve opening with con has a constant radius of curvature. The leaf spring is in Direction biased away from the catch plate as the Valve seat on a sloping floor surface of a recess tion of the valve plate, the depth of the ver deepening increases from the clamping end.  

A similar valve is also known from DE 44 40 903 A1 known in which the leaf spring and the catch plate in a recess of the valve plate are lowered to the Reduce dead volume of the valve opening. The floor surface of the recess with valve opening and valve seat runs parallel or at an acute angle to Valve plate surface. The catch plate bends steadily away from the valve plate over its entire length.

From DE 42 26 587 A1 a compressor valve is included a leaf spring and a catch plate known Training an adherence of the leaf spring when opening the Valve should prevent. The profile of the Catch plate flat and / or curved sections, the latter also with constantly changing radii of curvature. The The catch plate is on both ends of the valve plate consolidates.

These known valves have the disadvantage that the Leaf spring at least partially ver in the valve plate lowers or the catch plate is attached on both sides. Both increase the flow resistance through the valve arrangement and thus reduces the efficiency of the Compressor. The recess in the valve plate for Inclusion of the leaf spring increases the cost of manufacture and reduces the rigidity of the valve plate. To the recessed leaf springs or befe at both ends constant catch plates around increases the turbulence of the Gas flow and thus the noise level. A higher one Noise level also occurs when the sheet stops spring on the catch plate during the opening movement on because the kinetic energy of the leaf spring in Ge vibrations causing noise is implemented.

The invention has for its object a Druckven til of the type mentioned, the Ge noise level during operation is lower, the Manufacturing is easier and the efficiency of the Compressor increased.

According to the invention, this object is achieved in that the catch plate is curved away from the valve opening and each stiffener one by the same amount carry down over the clamping part of the catch plate protruding projection of the catch plate forms.

With this shape, the catch plate tends less Vibrations when the leaf spring when opening the Valve attaches very quickly to the catch plate. Further each stiffening element acts as a support element that is supported on the valve plate and the catch plate in Biased direction away from the valve plate. Thereby the swingable free end section of the catch plate te shortened and the natural vibration frequency of the catch plate increased. In particular, the natural frequency of the Catch plate be so high that, if necessary, by the Striking the leaf spring on the catch plate excited Natural vibrations of the catch plate above the audible range and therefore do not interfere.

It is preferably ensured that the stiffeners elements on the side of the valve plate facing the valve plate Leaf spring next to the clamping part of the leaf spring protrude.

It is preferably ensured that the leaf spring three from its clamping part to its free end extended parts, a middle part and two side parts and that the side parts in the transverse direction  Have a distance from the middle part and the stiffening element mente on the side parts and only the middle part with a contact surface of the part of the catch plate comes to the plant. This has the advantage that the contact part of the catch plate over the stiffening element only supported on the side parts of the leaf spring, that are not bent themselves. The amount of reinforcement tion elements (projections) do not need to un Different thicknesses of the leaf spring adapted to who but can be the same for all leaf spring thicknesses stay.

Another increase in stiffness (constant spring te) and thus increase the natural vibration frequency of the Leaf spring can be achieved when the attachment part the catch plate has a corrugated cross-sectional profile.

It is also advantageous if the width of the plant part the catch plate at its opposite the valve opening end is less than that of the clamping part. because through increases the available for gas flow standing free cross-sectional area, so that the Strö resistance of the pressure valve and the number of Places with large flow rate gradients minimized and therefore turbulence in the flow and the resulting flow noise is reduced become. A correspondingly reduced flow wi the state allows one large passage per piston stroke larger amount of gas and consequently increases the efficiency of the compressor.

A further development can be that the width the on opening the valve with the leaf spring location coming bearing surface of the plant part of the catch plate over the entire length of the contact surface smaller  than the smallest width of the with the contact surface Plant coming part of the leaf spring is. To this The leaf spring becomes stuck to the Catch plate avoided to prevent the Closing movement of the leaf spring is delayed and compressed gas flow back into the cylinder and thus the effect degree of the compressor would be reduced. The contact surface the plant part is narrower than that of the Blattfe it should be at least so wide that the Leaf spring not at their when opening the valve Bends longitudinal edges relative to the catch plate.

Then it can be ensured that the curvature radius of the contact surface of the contact part of the catch plate constantly changes towards the free catch plate end and in this direction in the plant part with a section increasing curvature a section with decreasing Curvature follows. This type of curvature of the contact surface the contact part of the catch plate away from the valve plate causes a continuous application of the leaf spring their opening movement towards the free catch plate end. This causes vibration and impact noises shunned that would arise if the free end of the sheet spring first on the contact surface of the catch plate meets. Which continues in the two sections Lich changing radii of curvature of the contact surface of the Catch plate results in a particularly low-noise valve, at the same time due to an optimal time Control of opening and closing movements of the Leaf spring a better compressor efficiency si cherstellt.  

It has turned out to be easy to manufacture proven to be advantageous if the contact surface of the Catch plate between their clamping part and their first curved section has a straight section, the one at a distance from and above the bottom of the clamping part. This way a gap corresponding to the distance between the top side of the leaf spring and the straight section of the on bearing surface of the plant part of the catch plate and a Edge between the bottom of the clamping part and the Contact surface of the system part. This will make a defi clamping surface consisting of the underside of the Clamping part and the end face of the stiffening element elements, ensured. The distance is preferably in the range between 0 and a maximum value of approximately 0.5 mm.

The leaf spring is on the catch plate Valve plate attached, the leaf spring an on Clamping part with openings for carrying out fastenings elements, for example rivets, and the opening with corresponding openings in the clamping part of the Collapse the catch plate. The clamping part of the sheet spring follows a narrow intermediate part, which is their one clamping part connects with a round head part. The Headboard closes the valve opening, and its size is adapted to the size of the valve seat, so that Head part just covers the valve opening. The width The intermediate part of the leaf spring is in the transverse direction tion measured distance between the stiffening elements elements of the catch plate adjusted so that the leaf spring in between on the contact surface of the contact part of the Can create catch plate. This design of the sheet spring results in a low stiffness of the leaf spring  with small valve openings so that the leaf spring even with a small overpressure in the cylinder of the Ven lift off the seat and the valve is opened. Despite the the leaf spring has a low rigidity Quickly responding valve due to the low movement mass of the leaf spring.

According to the invention, it is possible to cost a pressure valve cheap to produce from a few individual parts, the is at the same time quiet and the efficiency of the Compressor increases. The catch plate can be easily Way by machining a metal part or manufactured by other processes to For example by casting, sintering, eroding, punching or Shape.

Alternatively, the catch plate and the leaf spring can be made from Plastic or composite materials, for example game fiber-reinforced plastic, can be manufactured and it is also possible to sandwich the catch plate in Construction from several different materials put.

The invention and its developments will be next More preferred with reference to the accompanying drawings Exemplary embodiments described in more detail. Show it:

Fig. 1 is a plan view of a receiving plate of a first embodiment of a pressure valve for a compressor according to the invention,

Fig. 2 shows the cross section II-II through the trap plate according to Fig. 1,

See ge from the side of Fig. 3, the catch plate of Fig. 1,

Fig. 4 is a side view of a catching plate and designed as a leaf spring closure member of a second embodiment of he inventive pressure valve, wherein the leaf spring takes up the closed position,

Fig. 5 shows the encircled section of FIG. 4 in an enlarged scale,

Fig. 6 seen the catch plate of FIG. 4 from the bottom,

Fig. 7 is a diagram of the course of processing the curvature of the catch plate of Fig. 4 in its longitudinal Rich,

Fig. 8 is a bottom view of a leaf spring vorherge prospective embodiments of the erfindungsge MAESSEN pressure valve,

Fig. 9 is a plan view of an over the vorheri gen embodiments somewhat modified leaf spring,

Fig. 10 is a bottom view of a relation to the preceding embodiments, some abgewan punched catching plate which cooperates with the leaf spring of FIG. 9,

Fig. 11 is a perspective bottom view of the catcher plate shown in FIG. 10,

Fig. 12 shows the section XI-XI of Fig. 10 and

Fig. 13 the circled in Fig. 12 section of the catch plate on an enlarged scale.

Figs. 1 to 3 and 6 represent only a Fangplat te 1 of a pressure valve of the invention for a hermetic compressor is, the least-cylinder piston unit having a, whose cylinder is closed by a (not shown) the valve plate with minde least a valve opening , The Ven tilplatte is covered by a bilendende the valve closure part bil, in Figs. 4 and 5 additionally shown leaf spring 13 , the opening movement is limited by the catch plate 1 . The catch plate 1 and the leaf spring 13 are clamped on one side on the valve plate, the catch plate 1 having at least one clamping part 2 and a curved part 3 of the valve opening away. In the clamping part 2 , two openings 4 and 5 elements for carrying out fastening elements, for. B. rivets, through which the catch plate 1 is connected to the valve plate of the compressor. At the lateral edges of the plant part 3 , two stiffening elements 6 and 7 are formed, which simultaneously act as support elements. As shown in FIGS . 2, 4 and 5, the reinforcing elements 6 and 7 extend downward, ie in the direction of the valve plate or the leaf spring 13, not shown, over the underside 12 of the clamping part 2 and also up to the leaf spring 13 , prior to attachment of catch plate 1 and the leaf spring 13 to the valve plate, out, so that the end faces te 8 and 9 of Versteifungselemen 6 and 7, after the attachment of catch plate 1 and the leaf spring 13 on the valve plate, the plate supported on the valve , Fig. 2 also shows the cross section of the contact part 3 with the contact surface 10 and the Ver stiffening elements 6 and 7 and the cross-sectional profile 11 of the catch plate 1 , which is approximately trapezoidally corrugated on both sides.

When the catching plate according to FIGS. 1 to 3 the Appendices has geteil 3 according to FIG. 3 shows a ge over its entire length curved bearing surface 10 for the leaf spring 13.

In the embodiment of the catch plate 1 according to FIGS. 4 to 6, the contact surface 10, on the other hand, has a straight section 14 , see in particular FIGS . 5 and 6, and two sections 16 and 17 adjoining it towards the free end of the plant part.

As FIG. 5 shows more clearly, the straight-line section 14 extends at a distance A above the underside 12 of the clamping part 2 , an edge 15 being formed at the transition from the clamping part 2 to the contact part 3 .

FIGS. 4 and 5 more clearly show, in schematic form which serves as a valve seal part the leaf spring 13 in the unloaded state, to the lower position of the end faces 8, 9 of the stiffening elements 6, to illustrate 7 in a plane beneath the underside of the leaf spring 13.

Fig. 6 shows the view of the catch plate 1 according to FIGS. 4 and 5 from below with the different sections 14 , 16 , 17 of the contact surface 10 , the contact surface 10 in section 16 increasing curvature and section 17 decreasing Has curvature. The dashed line in Fig. 6 represents the transition between the two sections 16 and 17 .

The course of the curvature K of the contact surface 10 of the catch plate 1 according to FIGS. 4 to 6 is shown in FIG. 7 in dependence on the path S along the contact surface 10 . In section 14 , therefore, the curvature K = 0, while it increases abruptly at the end of section 14 , in order then to rise continuously in section 16 and to decrease continuously in section 17 after a continuous transition between the two sections. The course of the curvature K results from the second derivation of the function of the longitudinal profile of the contact surface 10 .

Fig. 8 illustrates the leaf spring 13 as seen from below. It has a clamping part 18, a round head portion 20 and a the clamping part 18 with the head part 20 of the intermediate connecting member 19. In the clamping part 18 are two openings 21 and 22 , which are aligned with the openings 4 and 5 in the catch plate 1 , are designed to carry out fastening elements.

The head part serves to close the valve opening and has a diameter adapted to the valve seat, so that it just covers the valve opening. The width of the intermediate part 19 is the transverse spacing of the Versteifungse elements 6 , 7 adapted so that the leaf spring between the stiffening elements 6 and 7 can freely create the contact surface 10 of the catch plate 1 .

While according to Fig. 8, the width of the intermediate portion 19 is constant, it can also remove from the clamping part 18 to the head portion 20.

The width of the contact surface 10 on the underside of the contact part 3 is over the entire length of the contact surface 10 smaller than the smallest width of the leaf spring 13 , while the width of the contact part 3 decreases towards the free end. As a result, relatively large free cross-sectional areas are available to the gas flow when the valve is open, and the flow resistance of the pressure valve and the number of points with large speed gradients of the gas flow are reduced. This will reduce eddies and flow noises. The low flow resistance allows the passage of a larger amount of gas per piston stroke and thus results in a higher efficiency of the compressor.

The smaller width of the contact surface 10 than that of the leaf spring 13 prevents the leaf spring from adhering to the catch plate and thus a delay in the closing movement of the leaf spring and a backflow of compressed gas into the cylinder. This also increases the efficiency of the compressor.

The contact surface 10 is raised compared to the laterally adjacent surfaces of the catch plate 1 and we at least so wide that the leaf spring 13 can not bend around the longitudinal edges of the contact surface 10 .

During the operation of the compressor, the end faces 8 , 9 rest on the valve plate. As a result, the catch plate 1 is elastically pre-tensioned towards the valve plate. The free end portion of the catch plate 1 is practically somewhat shorter than the plant part 3 , so that only this section could possibly be set in vibration by the application of the leaf spring 13 on the plant part 3 . However, since it is relatively short and accordingly stiff, its Eigenschwwin supply frequency is very high, so that possibly occurring oscillations or vibrations of the catch plate 1 are outside the listening area and therefore do not disturb. In addition, the stiffness (spring constant) and thus the natural oscillation frequency Catch plate through the stiffening elements 6 , 7 and the corrugated cross-sectional profile 11 of the catch plate 1 he further increases.

The distance A results in a defined clamping surface of the catch plate 1 from the underside 12 of the clamping part 2 and the end faces 8 , 9 of the reinforcement elements 6 , 7 . The distance A is greater than 0 and is at most about 0.5 mm, ie 0 <A ## 0.5 mm.

In the catch plate 1 and the leaf spring 13 according to FIGS. 9 to 12, the same reference numbers have been used for parts that are the same as or correspond to the preceding ones.

The leaf spring 13 according to FIG. 9 differs from that according to FIG. 8 essentially only in that it has three parts which extend from its clamping part 18 towards its free end, a middle part 23 with the intermediate part 19 and the head part 20 and on both sides of the center part a respective side part 24 has 23, wherein the side parts 24 in the transverse direction have a distance from telteil with 23rd The stiffening elements 6 , 7 rest only on the side parts 24 , and the central part 23 comes only with the contact part 3 of the catch plate 1 to position. Here, the projections designed as reinforcing elements 6 , 7 are supported indirectly, ie via the side parts 24 and only via this, on the valve plate, not shown, so that the central part alone with the contact surface 10 of the contact part 3 of the catch plate 1 is an investment comes. This has the advantage that the height of the stiffening elements 6 , 7 does not have to be adapted to the respective thickness of the leaf spring, as in the case of the previous exemplary embodiments, in which the stiffening elements 6 , 7 are supported directly on the valve plate.

Claims (9)

1. Pressure valve for a compressor, in particular a hermetically sealed compressor, which has at least one piston-cylinder unit, the cylinder of which is closed by a valve plate with at least one valve opening, the valve opening by a leaf spring ( 13 ) as a valve closure part is covered, the opening movement of which is limited by a catch plate ( 1 ), the leaf spring ( 13 ) and catch plate ( 1 ) being clamped on one side on the valve plate and the catch plate ( 1 ) a clamping part ( 2 ), a system part bent away from the valve opening ( 3 ) and between its a clamping part ( 2 ) and the valve opening has at least one stiffening element ( 6 , 7 ), characterized in that the catch plate ( 1 ) is curved away from the valve opening and each stiffening element ( 6 , 7 ) one forms by the same amount down over the clamping part ( 2 ) of the catch plate ( 1 ) protruding projection of the catch plate ( 1 ).
2. Pressure valve according to claim 1, characterized in that the stiffening elements (6, 7) project beyond the facing of the valve plate side of the leaf spring (13) near the clamping part (18) of the leaf spring (13).
3. Pressure valve according to claim 1 or 2, characterized in that the leaf spring ( 13 ) three of ih rem clamping part ( 18 ) to its free end he stretched parts, a central part ( 23 ) and two Be tentteile ( 24 ), has, and that the side parts ( 24 ) in the transverse direction have a distance from the middle part ( 23 ) and the stiffening elements ( 6 , 7 ) abut the side parts ( 24 ) and only the middle part ( 23 ) with a contact surface ( 10 ) of the system partly ( 3 ) of the catch plate ( 1 ) comes to rest.
4. Pressure valve according to one of claims 1 to 3, characterized in that the contact part ( 3 ) of the catch plate has a corrugated cross-sectional profile ( 11 ).
5. Pressure valve according to one of claims 1 to 4, characterized in that the width of the system part ( 3 ) of the catch plate ( 1 ) at its end opposite the ventilating opening is less than that of the clamping part ( 2 ).
6. Pressure valve according to claim 5, characterized in that the width of the surface when opening the valve with the leaf spring ( 13 ) comes to rest bearing surface ( 10 ) of the contact part ( 3 ) of the catch plate ( 1 ) over the entire length of the bearing surface ( 10 ) is smaller than the smallest width of the part of the leaf spring ( 13 ) coming into contact with the contact surface ( 10 ).
7. Pressure valve according to one of claims 1 to 6, characterized in that the radius of curvature of the contact surface ( 10 ) of the contact part of the catch plate te to the free catch plate end changes continuously and in this direction in the contact part ( 3 ) a section from ( 16 ) with increasing curvature follows a section ( 17 ) with decreasing curvature.
8. Pressure valve according to claim 7, characterized in that the contact surface ( 10 ) of the catch plate ( 1 ) between its clamping part ( 2 ) and its first curved section ( 16 ) has a straight section ( 14 ) which is at a distance (A ) from and above the underside ( 12 ) of the clamping part ( 2 ).
9. Pressure valve according to one of claims 1 to 8, characterized in that the leaf spring ( 13 ) between its clamping part ( 18 ) and serving to close the valve opening serving head part ( 20 ) has an intermediate part ( 19 ) which the clamping part ( 18 ) the leaf spring ( 13 ) and the head part ( 20 ) binds ver and has a constant or to the head part ( 20 ) decreasing width.
DE2000123455 1999-05-22 2000-05-12 Pressure valve for a compressor Expired - Fee Related DE10023455C2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19923732 1999-05-22
DE2000123455 DE10023455C2 (en) 1999-05-22 2000-05-12 Pressure valve for a compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2000123455 DE10023455C2 (en) 1999-05-22 2000-05-12 Pressure valve for a compressor

Publications (2)

Publication Number Publication Date
DE10023455A1 DE10023455A1 (en) 2001-01-25
DE10023455C2 true DE10023455C2 (en) 2002-06-20

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
DE2000123455 Expired - Fee Related DE10023455C2 (en) 1999-05-22 2000-05-12 Pressure valve for a compressor

Country Status (1)

Country Link
DE (1) DE10023455C2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006058990A1 (en) * 2006-12-14 2008-06-19 Danfoss Compressors Gmbh - Valve for a reciprocating compressor, especially useful for a hermetically sealed coolant compressor includes inflow region, and plate spring with restricting unit is very efficient and takes up little space

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10157234C1 (en) * 2001-11-22 2003-07-17 Knf Neuberger Gmbh Oscillating displacer

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2451207A1 (en) * 1974-10-29 1976-05-06 Bosch Siemens Hausgeraete Valve seat plate for a piston compressor, especially kaelteverdichter
DE2640054A1 (en) * 1976-09-06 1978-03-16 Sundstrand Corp Discharge and inlet valves of refrigeration compressor - are held to valve plate by common fixing pin
DE4226587A1 (en) * 1991-08-13 1993-02-18 Toyoda Automatic Loom Works Compressor discharge flap valve - has inclined stop which changes angle in region of valve flap attachment for progressive action
DE4440903A1 (en) * 1994-07-27 1996-02-01 Bitzer Kuehlmaschinenbau Gmbh Gas compressor
DE19524906A1 (en) * 1995-07-08 1997-01-09 Pierburg Ag Check valve for vacuum pump - spring strip opening limiter made from embossed or sheet stamped section and in stop region of spring strip has elongated hole
EP0774582A1 (en) * 1995-11-14 1997-05-21 Sanden Corporation Valved discharge mechanism of a fluid displacement apparatus
EP0699837B1 (en) * 1994-09-02 1998-06-03 Carrier Corporation Reed valve with tapered leg and dual radius valve stop

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2451207A1 (en) * 1974-10-29 1976-05-06 Bosch Siemens Hausgeraete Valve seat plate for a piston compressor, especially kaelteverdichter
DE2640054A1 (en) * 1976-09-06 1978-03-16 Sundstrand Corp Discharge and inlet valves of refrigeration compressor - are held to valve plate by common fixing pin
DE4226587A1 (en) * 1991-08-13 1993-02-18 Toyoda Automatic Loom Works Compressor discharge flap valve - has inclined stop which changes angle in region of valve flap attachment for progressive action
DE4440903A1 (en) * 1994-07-27 1996-02-01 Bitzer Kuehlmaschinenbau Gmbh Gas compressor
EP0699837B1 (en) * 1994-09-02 1998-06-03 Carrier Corporation Reed valve with tapered leg and dual radius valve stop
DE19524906A1 (en) * 1995-07-08 1997-01-09 Pierburg Ag Check valve for vacuum pump - spring strip opening limiter made from embossed or sheet stamped section and in stop region of spring strip has elongated hole
EP0774582A1 (en) * 1995-11-14 1997-05-21 Sanden Corporation Valved discharge mechanism of a fluid displacement apparatus

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006058990A1 (en) * 2006-12-14 2008-06-19 Danfoss Compressors Gmbh - Valve for a reciprocating compressor, especially useful for a hermetically sealed coolant compressor includes inflow region, and plate spring with restricting unit is very efficient and takes up little space
DE102006058990B4 (en) * 2006-12-14 2016-08-18 Secop Gmbh Valve for a reciprocating compressor

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Publication number Publication date
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