DE102021118692A1 - Device for controlling a flow rate of a gaseous fluid of a device for compressing the fluid - Google Patents

Abstract

The invention relates to a device for controlling a flow of a gaseous fluid through at least one outlet opening (15), in particular a valve, of a device for compressing the gaseous fluid. The device for controlling the flow has a lamellar valve element (16) with a longitudinal extent z and a fastening area (17) and a closing area (18). The valve element (16) is fixed at a first end with the fastening area (17) on a wall with the at least one outlet opening (15) in an area of an edge of the outlet opening (15) and with a free second end formed distally to the first end the at least one outlet opening (15) is arranged to be closable with the closing area (18). In addition, a stop element (21) is provided for limiting the travel of the valve element (16) when the at least one outlet opening (15) is opened. The valve element (16) has a connecting area (19) between the fastening area (17) and the closing area (18) with a transition area (20) to the closing area (18) and a variable width w along the longitudinal direction. The valve element (16) is designed with at least one means for stiffening, in particular for torsional stiffening.

Description

The invention relates to a device for controlling a flow of a gaseous fluid, in particular a valve, of a device for compressing the gaseous fluid. The device has a lamellar valve element, which is fixed with a first end to a wall of the device for compressing the fluid, specifically to an edge of an outlet opening, and closes the outlet opening with a free second end distal to the first end.

Compressors known from the prior art as devices for compressing the fluid for mobile applications, in particular for air conditioning systems in motor vehicles, for conveying refrigerant through a refrigerant circuit, also referred to as refrigerant compressors, are often designed as piston compressors with variable displacement or as scroll compressors, regardless of the refrigerant .

Conventional scroll compressors have, in addition to a housing, an immovable, stationary stator with a disc-shaped base plate and a spiral-shaped wall extending from one side of the base plate, and a movable orbiter also with a disc-shaped base plate and a spiral-shaped wall extending from a front side of the base plate on. The stator and the orbiter work together. The base plates are arranged in relation to one another in such a way that the spiral-shaped walls engage in one another.
The orbiter is moved on a circular path by means of an eccentric drive. During the movement of the orbiter, the walls of the stator and the orbiter touch at several points and form several consecutive, closed working spaces within the walls. Working spaces arranged adjacent to each other delimit volumes of different sizes. In response to the movement of the orbiter, the volumes and positions of the workspaces are changed. The volumes of the working spaces become increasingly smaller towards the middle of the spiral-shaped walls. The fluid compressed within the working chambers, which are becoming smaller, is discharged from the compression mechanism through an outlet opening formed in the stator. The outlet opening is closed by a valve and is opened in a targeted manner by a movement of the valve.

Valves of the outlet opening of scroll compressors known from the prior art are designed as so-called lamella valves which, in addition to the outlet of the fluid from the working chamber, also prevent the compressed and discharged fluid from flowing back into the working chamber.
The lamellar valve has a valve element designed as a lamella and a stop element for the valve element. The valve element can be destroyed, in particular break, under high load conditions of the compressor, ie at high speeds of the compressor and high delivery pressure of the fluid. The contour of the conventional lamellar valve element causes a high susceptibility to torsion of the lamella during opening and closing of the outlet opening. The torsional movement leads to an uneven and high load on the valve element on the one hand due to one-sided contact with the stator when the outlet opening is closed and on the other hand due to one-sided contact with the stop element when the outlet opening is open. As a result of the torsional movement and the associated one-sided loading, the valve element is subjected to an overload condition and breaks.

In the U.S. 5,345,970 A a valve stop of an exhaust valve is disclosed. The profile of the valve stop of the exhaust valve is designed according to the maximum bending stress or the maximum allowable fatigue stress of the valve element. The impact of the valve element on the valve stop always occurs when the valve element has the lowest kinetic energy and the highest potential energy, so that the lowest possible kinetic energy is transferred to the valve stop.

The object of the present invention is to provide a device for controlling the flow of the gaseous fluid through an outlet opening, especially a valve for the outlet opening, a device for compressing the gaseous fluid, in particular a compressor of a refrigerant circuit of an air conditioning system, for example for use in motor vehicles , to provide. The valve should have durability under high load requirements, such as high compression pressure and high speed. In particular, the susceptibility to torsion of the valve element and the stress concentrations along the valve element should be minimal in order to maximize the service life of the valve element. The cost of manufacturing the valve and running the compressor should be minimal.

The object is achieved by a device according to the invention for controlling a flow of a gaseous fluid through at least one outlet opening, in particular a valve, of a device for compressing the gaseous fluid. The device for controlling the flow of the gaseous fluid has a lamellar valve element with a longitudinal extension z in a longitudinal direction and a fastening area and a closing area. The valve element is fixed at a first end with the fastening area on a wall with the at least one outlet opening of the device for compressing the gaseous fluid, specifically in an area of an edge of the outlet opening. With a free second end formed distally to the first end, the valve element with the closing region is arranged so that the at least one outlet opening can be closed.
The device for controlling the flow of the gaseous fluid also has a stop element for limiting the travel of the valve element when the at least one outlet opening is opened.

A lamella is to be understood as meaning a thin plate which is preferably punched out of sheet metal. The sheet is a rolled metal product whose width and length are much greater than the wall thickness, ie the thickness.

According to the conception of the invention, the valve element between the attachment area and the closing area has a connecting area with a transition area to the closing area and along the longitudinal direction of the longitudinal extent z perpendicular to the longitudinal direction a variable width w. The connecting area of the valve element is formed with a smaller width w than the closing area.
According to the invention, the valve element is provided with a means for stiffening, in particular for torsional stiffening. The means for torsional stiffening serves to increase the torsional stiffness of the valve element. In this case, at least one means for stiffening is preferably formed in the transition area of the valve element.

und $${\text{Y}}_{\text{max}}=\mathrm{0,6924}{\text{x}}^3-\mathrm{2,1953}{\text{x}}^2+\mathrm{3,1445}\text{x}-\mathrm{0,0001}$$

mit x = L/z und Y = L/w bestimmt wird. Die Position L = 0 beschreibt einen Bereich eines Übergangs von einem geraden in einen gebogenen Abschnitt des Anschlagelements, auch als Einspannpunkt bezeichnet, während z die Längsausdehnung zwischen dem Einspannpunkt des Anschlagelements und einem Mittelpunkt des Schließbereichs des Ventilelements beschreibt. Bei L = z weist L den Maximalwert auf und x = 1.
Der zwischen dem Verbindungsbereich und dem Schließbereich ausgebildete Übergangsbereich ist mit einem Übergangsradius R ausgebildet.According to a development of the invention, the width w is dependent on a length L, starting at the end of the fastening area of the valve element, and lies within a range from Ymin to Ymax, which can be determined by means of the relationships $${\text{Y}}_{\text{at least}}=3.3234{\text{x}}^4-5.6596{\text{x}}^3+0.4485{\text{x}}^2+3.5378\text{x}+0.0024$$

and $${\text{Y}}_{\text{Max}}=0.6924{\text{x}}^3-2.1953{\text{x}}^2+3.1445\text{x}-0.0001$$

with x = L/z and Y = L/w. The position L=0 describes an area of a transition from a straight to a curved section of the stop element, also referred to as the clamping point, while z describes the longitudinal extent between the clamping point of the stop element and a midpoint of the closing region of the valve element. At L = z, L has its maximum value and x = 1.
The transition area formed between the connecting area and the closing area is formed with a transition radius R.

According to a preferred embodiment of the invention, the valve element has a strip-shaped primary valve element and at least one strip-shaped secondary valve element. The primary valve element and each secondary valve element are each arranged to be able to close an outlet opening. If the valve element is designed without at least one secondary valve element, the primary valve element is simply referred to as the valve element.

The primary valve element and the at least one secondary valve element of the valve element are advantageously arranged aligned in a common plane.

The primary valve element and the at least one secondary valve element of the valve element are preferably connected to one another at the first ends, forming the fastening area of the valve element.

If the valve element is designed with at least two secondary valve elements, the secondary valve elements are preferably arranged on both sides next to the primary valve element, so that the primary valve element is always positioned between two secondary valve elements.

A further advantage of the invention is that the valve element is designed with a constant wall thickness. The wall thickness can have values in the range from 0.10 mm to 0.60 mm, in particular in the range from 0.254 mm to 0.60 mm or 0.25 mm to 0.30 mm.

According to a development of the invention, a contact surface of the stop element and a surface of the valve element pointing towards the stop element are designed to correspond to one another. The contact surface of the stop element can correspond in shape and dimensions to the surface of the valve element facing the stop element or be larger than the surface of the valve element facing the stop element.

According to a further advantageous embodiment of the invention, the transition radius R of the transition area of the valve element has values in the range from 50 mm to 300 mm. A ratio of the longitudinal extension z of the valve element to the transition radius R can be in the range from 0.06 to 0.36.

A ratio of a stroke distance d of the valve element as a distance between the center point of the closing area of the valve element on the surface facing the stop element in the closed state perpendicular to the surface of the stop element pointing to the valve element to a diameter s of a cross section of the outlet opening is preferably at least 0.26.

A torsion angle φ relative to the nominal orientation of the valve element, in particular about an axis of the valve element running in the longitudinal direction, preferably has values in the range from 0° to 1° when opening or closing the outlet opening.

The advantageous embodiment of the invention enables the use of the device for controlling the flow of the gaseous fluid through at least one outlet opening in a device for compressing the gaseous fluid, in particular a refrigerant. The device for compressing the gaseous fluid is advantageously designed as a scroll compressor.

The device according to the invention for controlling the flow of the gaseous fluid, designed for example as a teardrop-shaped outlet plate and shape-optimized lamellar outlet valve, satisfies the increased load requirements of a scroll compressor, in particular an electrically driven one.
To prevent the valve element from being destroyed, specifically from breaking, its torsional movement is minimized in order to ensure uniform contact of the valve element on the contact surfaces that limit the overall movement. The torsional rigidity of the valve element is increased by modifications in shape and thickness, such as an enlarged transition radius in the transition area from the closing area to the connecting area compared to conventional valve elements. With the higher torsional rigidity, the torsional energy of the torsional movement is effectively dissipated. Within the stroke path or the valve path, the torsional movement can be dissipated in such a way that uniform contact between the valve element and the corresponding travel-limiting contact surfaces is ensured.

With an enlarged surface of the valve element, damping of the movement of the valve element is also effected, which results from the displacement of the compressed fluid and the overcoming of the fluid resistance. Depending on the rigidity requirement, the material thickness of the valve element can also be increased.

• - maximale Haltbarkeit auch unter hohen Lastanforderungen, wie hohen Drehzahlen, beispielsweise oberhalb von 8600 min^-1, des Verdichters über einen maximalen Zeitraum,
• - minimale Torsionsanfälligkeit und minimale Spannungskonzentrationen entlang des Ventilelements durch gleichmäßige Belastung des Ventilelements infolge optimierter Ventilkinematik während des Öffnens und Schließens,
• - minimale Schallemissionen, insbesondere infolge Körperschall und Vibrationen, durch Dämpfen der Ventilelementkontakte mit den Anlageflächen und
• - mögliche Serienfertigung bei minimalen Kosten bei der Herstellung des Ventilelements und dem Betrieb der Vorrichtung zum Verdichten des gasförmigen Fluids.

In summary, the device according to the invention for controlling the flow of the gaseous fluid has various other advantages:

• - maximum durability even under high load requirements, such as high speeds, for example above 8600 min ^-1 , of the compressor over a maximum period of time,
• - minimal susceptibility to torsion and minimal stress concentrations along the valve element through uniform loading of the valve element as a result of optimized valve kinematics during opening and closing,
• - Minimum noise emissions, in particular due to structure-borne noise and vibrations, by dampening the valve element contacts with the contact surfaces and
• - possible series production with minimal costs in the manufacture of the valve element and the operation of the device for compressing the gaseous fluid.

• 1: einen Ausschnitt eines Verdichtungsmechanismus mit einem Lamellenventil eines Scrollverdichters in einer seitlichen Schnittdarstellung,
• 2a und 2b: jeweils ein Ventilelement eines Lamellenventils aus dem Stand der Technik in perspektivischer Ansicht und in einer Draufsicht,
• 2c: einen Schließbereich eines Ventilelements eines Lamellenventils aus dem Stand der Technik in einer Draufsicht,
• 3a: ein Ventil einer Auslassöffnung mit einem Ventilelement und einem Anschlagelement im geschlossenen Zustand der Auslassöffnung in einer seitlichen Schnittdarstellung,
• 3b: Torsionsbewegung des Ventilelements während des Öffnens des Ventils in einer Frontansicht in Richtung eines Befestigungsbereichs des Ventilelements,
• 3c: Torsionsbewegung des Ventilelements während des Schließens des Ventils in einer Frontansicht in Richtung des Befestigungsbereichs des Ventilelements,
• 4: ein Ventil mit einem Ventilelement und einem Anschlagelement im entspannten Zustand des Ventilelements in perspektivischer Ansicht,
• 5: eine Detailansicht eines Primärventilelements des Ventilelements und des Anschlagelements in einer Draufsicht,
• 6a und 6b: Ausführungsformen des Ventilelements jeweils in einer perspektivischen Ansicht sowie
• 7a und 7b: die Form des Ventilelements als Verhältnis der Länge zur Breite des Ventilelements abhängig von der relativen Längsausdehnung des Ventilelements in Längsrichtung.

Further details, features and advantages of the invention result from the following description of exemplary embodiments with reference to the associated drawings. Show it:

• 1 : a detail of a compression mechanism with a reed valve of a scroll compressor in a lateral sectional view,
• 2a and 2 B : in each case a valve element of a reed valve from the prior art in a perspective view and in a plan view,
• 2c : a closing area of a valve element of a reed valve from the prior art in a plan view,
• 3a : a valve of an outlet opening with a valve element and a stop element in the closed state of the outlet opening in a lateral sectional view,
• 3b : Torsional movement of the valve element during opening of the valve in a front view in the direction of a fastening area of the valve element,
• 3c : Torsional movement of the valve element during valve closing in a front view towards the fastening area of the valve element,
• 4 : a perspective view of a valve with a valve element and a stop element in the relaxed state of the valve element,
• 5 : a detailed view of a primary valve element of the valve element and the stop element in a plan view,
• 6a and 6b : Embodiments of the valve element each in a perspective view and
• 7a and 7b : the shape of the valve element as a ratio of the length to the width of the valve element as a function of the relative lengthwise extent of the valve element in the longitudinal direction.

In 1 a section of a compression mechanism with a lamellar valve of a scroll compressor is shown in a lateral sectional view.
The scroll compressor 1 comprises a casing 2, an immovable, stationary stator 3 having a disk-shaped base plate 3a and a spirally formed wall 3b extending from one side of the base plate 3a, and a movable orbiter 4 having a disk-shaped base plate 4a and a wall extending from a Front of the base plate 4a extending, spirally formed wall 4b. Stator 3 and orbiter 4, which are also referred to as stationary or fixed spiral 3 or as movable spiral 4, work together. The base plates 3a, 4a are arranged relative to one another in such a way that the wall 3b of the stator 3 and the wall 4b of the orbiter 4 mesh.

The movable spiral 4 is moved on a circular path by means of an eccentric drive. During the movement of the spiral 4, the walls 3b, 4b touch at several points and form several consecutive, closed working spaces 5 within the walls 3b, 4b, with working spaces 5 arranged adjacent to each other delimiting volumes of different sizes. In response to the movement of the orbiter 4, the volumes and positions of the workspaces 5 are changed. The volumes of the working spaces 5 become increasingly smaller toward the center of the spiral-shaped walls 3b, 4b, which are also referred to as spiral walls.

The eccentric drive is formed from a drive shaft 6 , which rotates about an axis of rotation 7 , and an intermediate element 8 . The drive shaft 6 is supported on the housing 2 via a first bearing 9 . The orbiter 4 is eccentrically connected to the drive shaft 6 via the intermediate element 8, ie the axis of the orbiter 4 and the drive shaft 6 are offset from one another. The orbiter 4 is supported on the intermediate element 8 via a second bearing 10 .

The scroll compressor 1 also has a guide device 11 which prevents the movable scroll 4 from rotating and allows the movable scroll 4 to revolve.

Inside the housing 2 there is also a wall 12 which is fixed to the housing 2 and is also referred to as the counter wall. A counter-pressure area 13 is formed between the wall 12 and the movable spiral 4 . Due to the counter-pressure prevailing within the counter-pressure area 13, the movable spiral 4 is pressed with a force against the wall 12, which is fixed to the housing 2, fixed spiral 3 pressed. The counter-pressure area 13 is sealed off from a suction area 14 by a sealing element arranged between the movable spiral 4 and the counter-wall 12 .

The fluid to be compressed is sucked into the working chambers 5 through the intake area 14 and compressed as a result of the movement of the orbiter 4 relative to the stator 3 . The compressed fluid is discharged from the working chambers 5 through an outlet opening 15 formed in the stator 3 . The outlet opening 15 is closed and opened by means of a valve element 16 designed as a lamella.

From the 2a and 2 B shows in each case a valve element 16 ′ of a reed valve from the prior art in a perspective view and in a plan view.
The valve element 16', which is in the form of a stamped sheet metal, is formed from a primary valve element 16a', also referred to as the main valve element, and two secondary valve elements 16b, which are also referred to as secondary valve elements. The secondary valve elements 16b are each arranged on both sides next to the primary valve element 16a'. The primary valve element 16a' and the secondary valve elements 16b are aligned in a common plane. Alternatively, the valve element 16′ can also only have a primary valve element without secondary valve elements.

Both the primary valve element 16a' and the secondary valve elements 16b are each in the form of a finger, which are connected to one another at first ends. The valve element 16' is fixed to the stator 3, in particular to the base plate 3a of the stator 3, in the area of the first ends of the primary valve element 16a' and the secondary valve elements 16b that are connected to one another, which is referred to as the fastening area 17 of the valve element 16'.

The primary valve element 16a′ and the secondary valve elements 16b each have a closing area 18 at the second ends formed distally to the first ends. The ends of the finger-shaped primary valve element 16a ′ and secondary valve element 16b are each connected to one another via a web-shaped connecting region 19 . Since the connecting portion 19 is formed with a narrower width than the closing portion 18, the primary valve element 16a' and the secondary valve elements 16b each have a spoon shape in plan view.

Like in particular 2c As can be seen, the closing area 18 and the connecting area 19 of the primary valve element 16a′ and the secondary valve element 16b are each connected to one another in a transition area 20, which in turn is formed in a radius, in particular a transition radius.

how 3a shows, in which the outlet opening 15 is disclosed in the closed state in a lateral sectional view, the valve has a travel-limiting stop element 21 for the valve element 16 in addition to the movable valve element 16 .

The valve element 16 arranged to close the outlet opening 15 is fixed in the fastening area 17 together with the stop element 21 on the base plate 3a of the stator 3, for example screwed on. The stop element 21 rests on the valve element 16 and the valve element 16 on the stator 3 . The valve element 16 is consequently fixed between the stator 3 and the stop element 21 .

The stop element 21 is arranged at a maximum distance from the stator 3 at the free end of the valve element 16 formed distal to the fastening area 17 . The distance between the stator 3 and the stop element 21 increases steadily in the direction of the free end.

The stop element 21 serves to limit the stroke d of the valve element 16 during the process of opening the outlet opening 15. In the open state, the valve element 16 preferably lies flat against the stop element 21. Depending on the pressure ratio on both sides of the valve element 16, the outlet opening 15 is closed or opened by a movement of the valve element 16.

The longitudinal extent of the valve element 16 between the clamping point of the stop element 21 and the center point of the closing area 18 of the valve element 16 is shown with z.

In the 3b and 3c a torsional movement of the valve element 16 during the opening or the closing of the valve is shown in a front view in the direction of the fastening area 17 of the valve element 16.

When opening and closing the outlet opening 15, the free cross section of which has a diameter s, the valve element 16 is twisted in each case due to the torsional movement relative to the contact surfaces of the corresponding components. Thus, when opening the outlet opening 15, the valve element 16 is twisted on first contact with the stop element 21, while when closing, the valve element 16 is twisted on first contact with the base plate 3a of the stator 3. In each case, there is one-sided contact of the valve element 16 on the contact surface of the component corresponding to the valve element 16 . The one-sided contact causes an uneven load on the valve element 16.

With a torsion angle φ of the valve element 16 in the range from 0° to 1°, the valve element 16 is loaded evenly.

the end 4 shows the valve with the valve element 16, in particular the shape-optimized primary valve element 16a and the secondary valve elements 16b, and the stop element 21 in the relaxed state of the valve element 16 in a perspective view. The valve element 16 is arranged in the “closed” position. 5 shows a detailed view of the shape-optimized primary valve element 16a in connection with the stop element 21 in a plan view.

In order to meet the increased load requirements of the compressor, for example at a speed greater than ⁸⁶⁰⁰ rpm or a high compression pressure, and the associated excessively high stress, which, among other things, results in the torsional movement of the valve element 16 during the opening and closing of the outlet opening 15 with the respective one-sided contact between the valve element 16 and the corresponding components with the valve element 16 and consequently the respective one-sided load, the susceptibility to torsion of the valve element 16, in particular of the shape-optimized primary valve element 16a, is minimized. The torsional rigidity of the primary valve element 16a of the valve element 16 is increased compared to conventional valve elements.

The transition radius R of the transition area 20 connecting the closing area 18 and the connection area 19, in particular of the primary valve element 16a, is very large, preferably at a maximum. In comparison to conventional valve elements with transition radii in the range from 2 mm to 10 mm, the transition radius R of the valve element 16 is approximately 10 times larger. Additionally or alternatively, the wall thickness of the lamellar or sheet-like valve element 16 is increased in comparison to conventional valve elements to values in the range of 0.1 mm to 0.6 mm, in particular 0.254 mm to 0.6 mm, depending on the rigidity requirements, in order to increase the torsional rigidity of the valve element 16 to increase.

The high torsional rigidity of the valve element 16 reduces the susceptibility to torsional movements and any torsional movements that may occur are quickly dissipated. This prevents the valve element 16 from coming into contact on one side with the contact surface of the corresponding component. The valve element 16 is loaded evenly.

With the increased torsional rigidity, the torsional movements that occur within the range of movement of the valve element 16 are dissipated in such a way that a more uniform contact is achieved between the valve element 16 and the stop element 21 and the base plate 3a of the stator 3 as the components corresponding to the valve element 16 and limiting travel.

At the same time, the effective area of the valve element 16 enlarged in this way has a damping effect, since when the outlet opening 15 is closed by the valve element 16, more fluid is displaced and when the outlet opening 15 is opened by the valve element 16, a greater fluid resistance is overcome, which reduces the speed of movement or the Reduced speed when the valve element 16 hits or impacts the stop element 21 or the stator 3 . This reduces the momentum and hence the overall stress on the valve element 16.

Due to the significantly higher load on the primary valve element 16a compared to the secondary valve element 16b, primarily only the primary valve element 16a is designed with regard to the shape, in particular with the large transition radius R.

The outer contour of the stop element 21 corresponds to the outer contour of the valve element 16, specifically to the outer contour of the primary valve element 16a, in order to achieve at least complete overlap when the valve element 16 hits the stop element 21. The plant area of the stop element 21 consequently corresponds to the surface of the valve element 16 facing the stop element 21 or is preferably larger than the surface of the valve element 16 facing the stop element 21, which in 5 is shown by the primary valve element 16a.

Also in the 6a and 6b 1, embodiments of the valve element 16 are each shown in a perspective view.

The primary valve elements 16a of the valve elements 16 have, as in the embodiments of the valve elements 16 according to FIGS 4 and 5 , each have a teardrop shape to increase the torsional stiffness and effective area of valve member 16 compared to conventional valve members. With the reduction in the susceptibility to torsion and the speed of movement of the valve element 16, the service life of the valve element 16 and thus of the valve and of the device for compressing the gaseous fluid is also increased.

The transition radius R of the transition area 20 between the closing area 18 and the connecting area 19, specifically of the primary valve element 16a, is in the range of 50 mm, according to FIG 6a , up to 300 mm, according to 6b . The material thickness or the wall thickness of the sheet metal valve element 16 is in the range from 0.10 mm to 0.60 mm, in particular in the range from 0.25 mm to 0.30 mm. If the transition radius R of the transition area 20 is 300 mm, a wall thickness of 0.25 mm is preferred.

In the 7a and 7b is the shape of the valve element 16, in particular the primary valve element 16a, as a ratio of a length L to a width w of a section of the valve element 16 depending on the relative longitudinal extension of the valve element 16 in the longitudinal direction as a ratio of the length L of the section of the valve element 16 to the longitudinal extension z of the Valve element 16 shown.

The design of the shape of the valve element 16 takes place in individual steps and sections. A section of the valve element 16 is characterized in each case with the length L and the local width w. The outermost edge of the web-shaped connecting region 19 serves as the basis for the length L of the section L as a transition from the straight to the curved section of the stop element 21, which is also referred to as the clamping point. The length L of the section is determined from this extreme edge to the corresponding position of the selected section. The width w always results at the position belonging to the length L, in the direction perpendicular to the longitudinal direction of the valve element 16. The respective change in the length L of the section for designing the shape of the valve element 16 is to be selected depending on the desired accuracy.

At the beginning of the design of the shape of the valve element 16, the longitudinal extent z of the valve element 16 is specified. Then the ratio between the individual lengths L of the sections and the longitudinal extension z is calculated by changing the length L: $$\text{x}=\text{L}/\text{e.g}.$$

und $${\text{Y}}_{\text{max},\text{bevorzugt}}=\mathrm{0,6924}{\text{x}}^3-\mathrm{2,1953}{\text{x}}^2+\mathrm{3,1445}\text{x}-\mathrm{0,0001}$$

mit $$\text{Y}=\text{L}/\text{w}$$

berechnet.With the ratio x and the length L of the section, the respectively associated width w of the individual sections is calculated using the relationships $${\text{Y}}_{\text{at least},\text{preferred}}=3.3234{\text{x}}^4-5.6596{\text{x}}^3+0.4485{\text{x}}^2+3.5378\text{x}+\mathrm{0.0024,}$$

and $${\text{Y}}_{\text{Max},\text{preferred}}=0.6924{\text{x}}^3-2.1953{\text{x}}^2+3.1445\text{x}-0.0001$$

with $$\text{Y}=\text{L}/\text{w}$$

calculated.

The shape of the valve element 16 is in the range of the preferred shape between Ymin and Ymax.

For a uniform loading of the valve element 16, in addition to the shape, the stroke d of the valve element 16, according to FIG 3a , which describes the distance between the center point of the closing area 18 of the valve element 16 on the surface facing the stop element 21 in the closed state of the outlet opening 15 in the direction perpendicular to the surface of the stop element 21 pointing to the valve element.

The stroke d of the valve element 16 is defined in particular as the vertical distance between the center of the closing area 18 in the closed state of the outlet opening 15 and a perpendicularly projected point on the surface of the stop element 21 facing the valve element 16 . The projection of the point consequently extends from the center of the closing area 18 of the valve element 16 onto the surface of the stop element 21.

The stroke d of the valve element 16 is dependent on the longitudinal extension z of the valve element 16, the transition radius R of the transition area 20 of the valve element 16 and the diameter s of the cross section of the outlet opening 15 and is decisive for the dissipation potential of the torsional movement of the valve element 16. If the stroke d of the valve element 16 is too small, the torsional movement of the valve element 16 is not completely reduced, which can lead to a one-sided contact of the valve element 16 on the contact surface of the corresponding corresponding component, in particular the stator 3 or the stop element 21.

erfüllen, während der Hubweg d des Ventilelements 16 der Bedingung $$\mathrm{0,26}\le \text{d}/\text{s}$$

folgen sollte.In order to ensure effective dissipation of the torsional movement, the valve element 16 should meet the following condition $$0.06\le \text{e.g}/\text{R}\le 0.36$$

meet while the stroke d of the valve element 16 of the condition $$0.26\le \text{i.e}/\text{s}$$

should follow.

The sheet-metal valve element 16 can, for example, have a shape with the following parameters: wall thickness of 0.15 mm, longitudinal extent z of 30 mm, width w of the connecting area 19 of 7 mm, transition radius R of the transition area 20 of 125 mm with a stroke d of 4 mm and a diameter s of the outlet opening 15 of 13 mm.

reference list

1

scroll compressor

2

housing

3

Stator, fixed spiral

3a

Fixed spiral base plate 3

3b

wall fixed spiral 3

4

Orbiter, moving spiral

4a

Movable spiral base plate 4

4b

wall movable spiral 4

5

working space

6

drive shaft

7

axis of rotation

8th

intermediate element

9

first camp

10

second camp

11

guiding device

12

wall

13

back pressure area

14

intake area

15

exhaust port

16, 16'

valve element

16a, 16a'

primary valve element

16b

secondary valve element

17

mounting area

18

locking area

19

connection area

20

transition area

21

stop element

i.e

stroke distance

R

transition radius

s

Diameter cross-section outlet opening 15

L

Length section valve element 16

w

Wide section valve element 16

x

Ratio between length L and width w

e.g

Longitudinal expansion valve element 16

φ

Torsion angle valve element 16

QUOTES INCLUDED IN DESCRIPTION

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Patent Literature Cited

• US5345970A [0005]

Claims (15)

Device for controlling a flow of a gaseous fluid through at least one outlet opening (15), in particular a valve, of a device for compressing the gaseous fluid, having - a lamellar valve element (16) with a longitudinal extent z and a fastening area (17) and a closing area ( 18), wherein the valve element (16) is arranged fixed at a first end with the fastening area (17) on a wall with the at least one outlet opening (15) in an area of an edge of the outlet opening (15) and with one distal to the first end formed free second end with the closing area (18), the at least one outlet opening (15) is arranged closable, and - a stop element (21) for limiting the travel of the valve element (16) when opening the at least one outlet opening (15), characterized in that that the valve element (16) between the fastening area (17) and the closing area (18) has a connection g area (19) with a transition area (20) to the closing area (18) and along the longitudinal direction of the longitudinal extension z perpendicular to the longitudinal direction has a variable width w, wherein the connecting area (19) has a smaller width w than the closing area (18), and that the valve element (16) is formed with at least one means for stiffening, in particular for torsional stiffening. device after claim 1 , characterized in that at least one means for stiffening in the transition region (20) of the valve element (16) is formed. device after claim 1 or 2 , characterized in that the width w is dependent on a length L, starting at the end of the attachment portion (17) of the valve member (16), within a range from Ymin to Ymax, which with $${\text{Y}}_{\text{at least}}=3.3234{\text{x}}^4-5.6596{\text{x}}^3+0.4485{\text{x}}^2+3.5378\text{x}+0.0024$$

and $${\text{Y}}_{\text{Max}}=0.6924{\text{x}}^3-2.1953{\text{x}}^2+3.1445\text{x}-0.0001$$

is determined with x=L/z and Y=L/w, so that the transition region (20) is formed with a transition radius R. Device according to one of Claims 1 until 3 , characterized in that the valve element (16) has a strip-shaped primary valve element (16a) and at least one strip-shaped secondary valve element (16b), the primary valve element (16a) and each secondary valve element (16b) having an outlet opening (15) that can be closed. device after claim 4 , characterized in that the primary valve element (16a) and the at least one secondary valve element (16b) are arranged aligned in a common plane. device after claim 4 or 5 , characterized in that the primary valve element (16a) and the at least one secondary valve element (16b) are connected to one another at first ends, forming the fastening area (17) of the valve element (16). Device according to one of Claims 4 until 6 , characterized in that the valve element (16) is formed with at least two secondary valve elements (16b), the secondary valve elements (16b) being arranged on both sides next to the primary valve element (16a). Device according to one of Claims 1 until 7 , characterized in that the valve element (16) has a constant wall thickness. device after claim 8 , characterized in that the wall thickness has values in the range from 0.10 mm to 0.60 mm, in particular in the range from 0.25 mm to 0.30 mm. Device according to one of Claims 1 until 9 , characterized in that a contact surface of the stop element (21) and a stop element (21) facing surface of the valve element (16) are designed to correspond to one another, the contact surface of the stop element (21) corresponding in shape and dimensions to the surface of the valve element (16) facing the stop element (21) or being larger than the surface of the valve element (16) facing the stop element (21). ). Device according to one of claims 3 until 10 , characterized in that the transition radius R of the transition area (20) has values in the range from 50 mm to 300 mm. Device according to one of claims 3 until 11 , characterized in that a ratio of the longitudinal extent z of the valve element (16) to the transition radius R has values in the range from 0.06 to 0.36 Device according to one of Claims 1 until 12 , characterized in that a ratio of a stroke d of the valve element (16) to a diameter s of a cross section of the outlet opening (15) is at least 0.26. Device according to one of Claims 1 until 13 , characterized in that a torsion angle cp of the valve element (16) when opening or closing the outlet opening (15) has values in the range from 0° to 1°. Use of the device according to any one of Claims 1 until 14 in a device for compressing a gaseous fluid, in particular a refrigerant.

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