INTAKE VALVE FOR THE INLET OF A COMPRESSOR ELEMENT AND COMPRESSOR AND COMPRESSOR ELEMENT FITTED THER

专利摘要:
Inlet valve comprising a housing (17) with an inlet (18) and an outlet (19) and an inner portion (17b) which, together with an outer portion (17a), delimits a flow channel (20) between inlet (18) and outlet (19) ), wherein this flow channel (20) can be closed by a valve (21), characterized in that this valve (21) comprises a piston (24) and valve element (25), the piston (24) being slidable in the housing (17) ) and is in communication with the outlet (19) and wherein the valve element (25) is formed by a valve stem piston (33) slidable in the piston (24) such that in the rest position the valve element (25) is passed through the piston (24) is pushed against a valve seat, with a chamber (41) enclosed between the valve stem piston (33) and the piston (23) which can come into fluid communication with the pressure vessel (8) and is provided with a blow-off outlet (42) which forms a fluid connection between the chamber (41) and the entrance (18), wherein the valve stem piston (33) is a byp shaft passage (44) which communicates with the chamber (41) and the side wall of the valve stem piston (33).
公开号:BE1025352B1
申请号:E2017/5641
申请日:2017-09-08
公开日:2019-02-05
发明作者:C/O Atlas Copco Airpower Naamloze Vennootschap Mertens Joris
申请人:Atlas Copco Airpower Naamloze Vennootschap；
IPC主号:

专利说明:

Inlet valve for the inlet of a compressor element and compressor and compressor element equipped with it.
The present invention relates to an inlet valve for the inlet of a compressor element.
In the world of compressors, inlet valve on the inlet of is well known for oil or the use of a compressor element fluid-injected compressors in which oil or other fluid is injected into the compressor element during the operation of the compressor for purposes of lubrication, cooling sealing between the rotating parts of becomes and / or the compressor element.
Such compressors comprise a motor-driven compressor element with an inlet for suction of a gas to be compressed and an outlet for the compressed gas to which a pressure line connects, which leads the compressed gas to a pressure boiler in which the compressed gas is buffered under pressure via a output from the pressure vessel to a consumer network.
The oil or other liquid present in the compressed gas is separated and collected in the pressure vessel and injected from there into the compressor element under the influence of the pressure built up in the pressure vessel.
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It is known to use an inlet valve or so-called unloader with such compressors to, when there is no consumption of compressed gas, to run the compressor element without load by closing the inlet with the inlet valve in order not to suck in and compress extra air and simultaneously releasing the pressure in the pressure vessel to the environment via the same inlet valve.
Because of this the pressure in the pressure vessel is as low as possible kept so that the compressor element is low in this case pressure resistance which is beneficial to it energy consumption during this phase of no-load running.
This method of running the compressor element without load is more energy-efficient for fixed-speed compressors in which the motor is always stopped when there is no consumption and is restarted when the consumption resumes.
Blowing off the pressure vessel is also applied at start-up to limit the pressure in the pressure vessel during this phase so that the start-up would require less power. This is also applied when shutting down and in the event of an emergency stop.
Another known application is that during the unloaded rotation the inlet valve is closed and a small amount of gas is recirculated from the pressure vessel to the inlet of the compressor element in order to pump this gas in a closed circuit and thus to circulate a closed circuit.
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BE2017 / 5641 minimum pressure in the pressure vessel required for adequate oil or liquid injection.
There are essentially two types of inlet valves, namely the spring-controlled inlet valves and the vacuum-controlled inlet valves.
With the spring-controlled inlet valves, the inlet valve is pushed open by the pressure in the pressure vessel and is closed again by means of a spring. Keeping the inlet valve closed requires considerable force. Such inlet valves have the disadvantage that they are relatively complex and contain many parts.
With the vacuum-controlled inlet valves, the opening and closing of the valve is controlled by means of several control pressure valves.
A danger with such inlet valves is that in the case of an emergency stop where, for example, the drive suddenly drops out, the inlet valve remains open, as a result of which the gas flows from the pressure vessel under the influence of pressure in the pressure vessel back in the reverse direction via the compressor element and thereby a amount of oil from the pressure vessel and spits out through the inlet. This entails that the inlet filter at the inlet of the compressor element is smeared with oil, which is of course not desirable.
To prevent this, such vacuum-controlled inlet valves are provided with an additional non-return valve which is one
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BE2017 / 5641 represents additional costs. Moreover, such inlet valves are also relatively complex and require a fairly complex control of the control valves.
An example of such a vacuum-controlled inlet valve is described in BE 1,015,079 in the name of the same applicant.
Yet another application in which an inlet valve is used is described in BE 1,021,804 of the same applicant, in order to prevent an oil-injected variable speed compressor from causing condensation to occur in the oil due to a too low temperature of the oil at stopping the engine, in which case the engine is not immediately stopped but is further driven with an open inlet valve in order to be able to use the compression heat of the compressed gas to heat up the oil.
In this case, a fairly complex control is required that uses at least two control valves, namely one for closing the inlet valve, one for condensate prevention and possibly an additional control valve to be able to blow off the pressure vessel when necessary.
The present invention has for its object to provide a solution to one or more of the aforementioned and other disadvantages.
To this end the invention relates to an inlet valve for the inlet of a compressor element of a compressor provided with a pressure vessel connected to the outlet of the
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BE2017 / 5641 compressor element, the inlet valve containing a housing with an outer part with an inlet for the inlet valve and an outlet for the inlet valve for connection to the inlet of the compressor element and an inner part that defines a flow channel between the inlet together with the outer part and the outlet of the inlet valve with which this channel can be closed by means of a valve which is pushed into a rest position by means of a spring against a valve seat of the inlet valve, characterized in that this valve is composed of a piston and a valve element cooperating therewith, the piston being slidably arranged in axial direction in a guide of the inner part of the housing and being pushed towards the valve seat by means of the aforementioned spring, the piston on the side remote from the valve seat being connected to the outlet of the inlet valve and with the valve element located on the other side of the piston and is formed by a valve stem piston and a head provided on the valve stem piston, the valve stem piston being coaxially slidably mounted in the piston to a certain depth which is limited by a stop which is such that the valve element by the piston is in rest position the valve seat is pushed under the influence of the aforementioned spring, an intermediate chamber being enclosed between the valve stem piston and the valve element being provided with at least one blow-off inlet via which the intermediate chamber can be put in fluid communication with the pressure vessel and at least one blow-off outlet which forms a permanent fluid connection between the intermediate chamber and the inlet of the inlet valve, wherein
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BE2017 / 5641 the valve stem piston further comprises a bypass passage which communicates with the intermediate chamber and which opens into the side wall of the valve stem piston, either directly or indirectly via a blow-off outlet of the intermediate chamber.
Such an inlet valve is easy to realize and contains few parts and yet allows to realize all the aforementioned applications with only one single control valve and without additional non-return valve for blowing off the pressure vessel, bypassing to maintain a minimum pressure in the pressure vessel and the condensate prevention in the oil.
The inlet valve can be used universally for compressors with a fixed speed or with a variable speed and / or with a condensate prevention function, whereby in the latter case even fewer control valves are required than known.
The double valve also fulfills the function of a non-return valve, so that no additional non-return valve is required to prevent oil from being spewed from the pressure vessel via the inlet and the inlet filter in the event of a sudden failure of the compressor element drive.
The spring ensures that the valve element and piston together act as a check valve, so that if no gas is sucked in due to drive failure, the inlet valve closes the inlet and therefore no oil can be blown out through the inlet while the blow-off is being vented from
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BE2017 / 5641 pure gas from the pressure boiler via the blow-off inlet and blow-off outlet always remains possible.
The inlet valve is preferably a valve with a vertical arrangement in which the axial direction of the piston and of the valve element are oriented vertically with the valve element above the piston.
In that case, the weight of the valve element helps to keep the inlet valve open.
Preferably, the valve stem is slidably fitted in the piston with a sliding fit without seals, so that the valve element can be slid in the piston without significant resistance. Moreover, this keeps the number of parts of the inlet valve limited.
Preferred, the aforementioned spring is the only spring of the inlet valve, which also limits the number of parts.
The inlet valve is preferably provided with an intermediate seal between the stop-forming collar of the wider head and the stop-forming edge of the piston.
This offers the advantage that the double valve can act as a one-piece non-return valve when the piston pushes the valve element against the valve seat under the influence of the spring, since in that case no pressure gas can escape between the piston and the valve element.
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In a particular aspect, the head of the valve element is provided at the contact zone with the valve seat with a head seal to have a better seal of the air inlet when the inlet valve is closed.
The head of the valve element is preferably covered with a sealing membrane to form the intermediate seal and the head seal.
The sealing membrane is preferably provided with a vent opening which forms a fluid connection between the aforementioned vent outlet of the intermediate chamber and the inlet of the inlet valve, so that gas can be vented out of the pressure vessel via the intermediate chamber and this vent opening.
The diameter of the head of the valve element at the location of the contact zone with the valve seat is preferably larger than the outside diameter of the valve stem piston of the valve element, this to prevent flapping of the inlet valve during the unloaded operation with blow-off or bypass.
The invention also relates to a compressor with a compressor element and a pressure vessel connected to the outlet of the compressor element which is provided with an inlet valve according to one of the preceding claims, wherein this inlet valve is in fluid communication via a blow-off line with a blow-off valve therein one blow-off inlet of the intermediate chamber of the inlet valve and wherein the inlet valve, in particular the blow-out exit and the bypass passage, are such
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BE2017 / 5641 dimensioned that, with the compressor element in unloaded operation with the inlet valve fully open and the blow-off valve open to blow off the contents of the pressure vessel via the inlet valve, the pressure after stabilization of the regime is between 0, 05 and 0.15 MPa.
This offers the advantage that in this way a sufficient pressure is maintained in the pressure vessel to also guarantee a sufficient oil supply under the influence of the boiler pressure to the compressor element during unloaded operation, on the one hand, and on the other hand to have a relatively low back pressure which ensures for a relatively low energy consumption in this no-load state.
Preferably, the shape and dimensions of the head of the inlet valve are selected such that during the loaded operation of the compressor element, the aforementioned blow-off valve in the blow-off line being closed and the inlet valve being open for allowing the compressor element to suck in gas via the inlet valve, the pressure difference between the static pressure at the inlet of the inlet valve and the static pressure in the intermediate chamber of the inlet valve creates a force on the valve element directed away from the valve seat.
In this way a force is generated by the flow of gas between the valve seat and the valve element which helps to keep the valve open.
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In the opposite case, the valve would be sucked back again by the flow, it is found in practice when, against all odds, the head of the valve element is given a streamlined convex shape with few charge losses.
It was therefore a surprise to find that the best results were achieved with a valve element whose head in the zone where the head of the valve element contacts the valve seat is formed by a square edge of the head of the valve element.
A shape that yields good results in testing is that in which the head of the valve element is essentially cylindrical at one end, the end circumferential edge of this cylindrical end forming the zone with which the head of the valve element in the closed state of the inlet valve comes into contact with the valve seat of the inlet valve housing.
The cylindrical head end may, for example, be flat with a plane extending perpendicular to the axial direction of the valve element.
For this purpose, the head of the valve element can be full with a passage to the blow-out exit of the intermediate chamber of the inlet valve or be at least partially hollow and spanned by the aforementioned sealing membrane which is provided with a blow-off opening.
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The housing of the inlet valve is preferably provided with a blow-off connection for the external connection of said blow-off line with the blow-off valve arranged therein, into which said blow-off line opens at the above-mentioned blow-off entrance of the intermediate chamber of the intake valve or of an intermediate chamber in communication with it such that this vent opening is constantly connected to the intermediate chamber of the inlet valve.
In this way, the intermediate chamber in all positions of the inlet valve can be connected to the pressure vessel by opening the aforementioned relief valve.
The invention is particularly applicable to an oil or liquid-lubricated compressor element, in which the operation of the inlet valve as a non-return valve is guaranteed at all times, thereby avoiding oil or liquid from coming off when the compressor element is stopped or accidentally stopped the pressure vessel would be blown out via the compressor element and the inlet valve, and this without the use of an additional non-return valve.
An inlet valve according to the invention can be used in a compressor with a drive of the compressor element with a fixed speed, wherein the bypass passage is indirectly via a blow-off outlet in fluid communication with the intermediate chamber of the inlet valve.
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12 BE2017 / 5641 In this case, the aforementioned relief valve may serve to do as a control element for switching between it load and unloaded rotation of the compressor element Bee
the fixed speed of the drive.
An inlet valve according to the invention can also be used with an oil-injected compressor with a variable speed drive of the compressor element, the bypass passage being directly in fluid communication with the intermediate chamber of the inlet valve.
In this case, the blow-off valve can serve as a control element to prevent condensation in the oil by, in the event of a risk of condensation, changing from loaded to unloaded by lowering the speed to an unloaded speed, continuing to drive the compressor element at a speed that is higher is then to open the idle speed and at the same time the relief valve until the danger of condensation has disappeared.
An advantage is that in that case only a single blow-off valve is sufficient to switch the compressor from loaded to unloaded and vice-versa and to control condensate prevention.
With the insight to better demonstrate the features of the invention, some preferred embodiments of an inlet valve according to the invention and of the invention are described below as an example without any limiting character.
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BE2017 / 5641 a compressor element and compressor equipped therewith, with reference to the accompanying drawings, in which:
figure 1 schematically represents a compressor with a compressor element with an inlet valve according to the invention;
Figure 2 is a perspective view of the inlet valve indicated by F2 in Figure 1;
figure 3 represents a section according to the line III-
III in figure 2 with the inlet valve at rest;
Figure 4 shows the inlet valve of Figure 2 in the disassembled state;
Figures 5 to 11 show different operating states of the inlet valve of Figure 3 included in a simplified diagram of the compressor of Figure 1;
Figure 12 shows a cross-sectional view like that of Figure 3 of a variant embodiment of an inlet valve according to the invention;
Figure 13 gives an overview of different forms of an inlet valve according to the invention.
The compressor 1 shown in Figure 1 is an oil-injected screw compressor comprising a compressor element 2 with a fixed speed drive 3.
The compressor element 2 is provided with an inlet 4 and with an outlet 5.
The inlet 4 is connected to an inlet filter 6.
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An inlet valve 7 according to the invention is mounted between the inlet 4 and the inlet filter.
At the outlet 5 is a busy chain 1 8 connected via a pressure line 9 that is connected on the entrance 10 of the pressure vessel 8. The pressure boiler 8 is provided with a output 11 with a pressure relief valve 12 on which one consumer network 13 is connected or can be connected that uses from
the gas supplied by the compressor element 2 under pressure.
The pressure vessel 8 is filled to a certain level with oil 14 which is injected in known manner under the influence of the pressure in the pressure vessel 8 via an injection line 15 at the location of one or more injection points 16 in the compressor element 2, inter alia for lubrication and cooling the compressor element 2.
The inlet valve 7 is shown in more detail in Figures 2 and 3.
It comprises a housing 17 with an outer portion 17a and an inner portion 17b mounted therein.
The external part 17a is provided with an inlet 18 for the inlet valve 7 which connects to inlet filter 6 and with an outlet 19 which connects to the inlet 4 of the compressor element 2.
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The inner portion 17b, together with the outer portion 17a, defines a flow channel 20 between the inlet 18 and the outlet 19 of the inlet valve 7, said flow channel 20 being closable by means of a valve 21 which, in the rest position of FIG. a spring 22 is pushed against a valve seat 23 of the housing 17 to close the inlet 18.
The valve 21 is according to the invention a double valve which is composed of a piston 24 and a valve element 25 cooperating with it.
The piston 24 is slidably arranged in axial direction X-X 'in a guide 26 of the inner portion 17b of the housing 17 and is pushed in the direction of the valve seat 23 by means of the aforementioned spring 22.
The axial direction X-X 'is oriented vertically in the example.
The piston 24 is on the underside 27 remote from the valve seat 23 in contact with the pressure / negative pressure in the inlet 4 of the compressor element 2.
The piston 24 is provided along its outer circumference with one or more pair of laterally projecting peripheral ribs 28 which each define a groove 29 in which an O-ring or other seal 30 is provided to form a seal between the piston 24 and its guide 25.
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In the illustrated example, an intermediate chamber 31 is delimited by the circumferential ribs 28 between the O-rings or other seals 30.
The piston 24 is hollow and comprises one or more blow-off ports 32 which form a fluid connection between the intermediate chamber 31 and the interior of the hollow piston 24.
The valve element 25 is arranged between the piston 24 and the valve seat 23.
The valve element 25 is formed by a valve stem piston 33 with which the valve element 25 is slidably mounted in the hollow piston 24 coaxially with the piston 24, and a head 34 provided on the valve stem piston 33 which limits the depth over which the valve element 25 can slide into the piston 24 by a stop formed in this case by, on the one hand, a stop-forming collar of the head 34 formed by the head 34 being wider than the valve stem piston 33, and, on the other hand, a stop-forming edge 36 cooperating therewith at the top of the piston 24.
The valve stem piston 33 is slidably mounted in the piston 24 with a sliding fit without any sealing.
The stop 35-36 is such that in the rest state of Figure 3, the valve element 25 with the peripheral edge of its upper end is pushed by the piston 24 against the valve seat 23 under the influence of the aforementioned spring 22.
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Preferably, the diameter A of the head 34 of the valve element 25 at the area of contact with the valve seat 23 is larger than the outer diameter B of the valve stem piston 33 of the valve element 25.
The valve element 25 is hollow with a bottom 37 facing the piston.
The head 34 of it valve element 25 is exaggerated through a sealing membrane that causes the formation from a head seal 38 to r site of the contact zone from it valve element 25 with the valve seat 23 and for the formation from
the intermediate seal between the valve element 25 and the piston 24 at the stop 35-36 when the valve element with its stop-forming collar 35 is slid against the stop-forming edge 36 of the piston 24.
It is clear that the seals 38 and 39 can also be replaced by separate seals or by the direct contact between the valve element 25 and the valve seat, on the one hand, and by the direct contact between the valve element 25 and the piston 24, on the other.
Note that in the illustrated example of Figure 3, the head 34 of the valve element is cylindrical with a flat head end formed by a portion of the sealing membrane 38 that covers the hollow valve element and extends perpendicular to the axial direction X-X '.
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An intermediate chamber 41 is enclosed between the valve stem piston 33 and the piston 24 which is in permanent fluid communication with the inlet 18 of the inlet valve 7 via a blow-off outlet 42 in the bottom 37 of the valve element 25 and a central blow-off opening 43 in the sealing membrane 38.
The valve stem piston 33 further comprises a bypass passage 44 which, just above the bottom 37 of the valve element 25, opens laterally between the stop-forming collar 35 of the valve element 25 and the stop-forming edge of the piston 24 when a valve is at rest as shown in Figure 3.
This bypass passage 44 is positioned indirectly via the hollow valve element 23 and the blow-off outlet 42 in the bottom 37 of
into the valve element41. connection to the intermediate room The housing 17 is provided of at least a blow-off connection 45 on which a blow-off pipe 4 is 6 connected that in fluid connection stands with the content
of the pressure vessel 8 above the level of the oil 14.
The blow-off connection 45 opens into the inlet valve at the level of the intermediate chamber 31, which itself is connected via the blow-off entrance 32 to the intermediate chamber 41.
A blow-off valve 47 is included in the blow-off line 46 which allows the blow-off line 46 to be opened or closed.
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The blow-off valve that is normally open is in this case an electro-valve and can be operated by means of a control 48.
Note that in the example of figure, the blow-off valve is the only valve.
The operation of the device 1 is like follows. Departing from stagnation with a inlet valve 7 in the resting state of figure 3 can the compressor 1 turn into started by the drive 3 te launch. This is used in the inlet 4 from it compressor element a underpressure built up that both the piston 24 as the inlet valve open downwards 1 draws against the pressure from the
spring 22 as shown in figure 5.
The pressure in the pressure vessel 8 then begins to build up. This pressure is connected via the open blow-off valve 47 to the intermediate chamber 41, which thereby also starts to be under pressure and pushes the valve element 25 upwards until closure of the inlet valve 7 as shown in Figure 6.
At that moment, no more gas is sucked in and gas is blown out of the pressure vessel 8 via the intermediate chamber 41 and the blow-off outlet 42 in the bottom 37 of the valve element 25 and the blow-off opening 43 in the sealing membrane 38 outwards via the inlet filter 6 such as is indicated by arrow C in Figure 6 and is
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BE2017 / 5641 simultaneously gas from the pressure vessel 8 to the inlet 4 of the compressor element 2 bypassed via the intermediate chamber 41 and the bypass passage 44 and thus back to the pressure vessel 8 as shown with arrow D in figure 6.
As a result, the pressure in the pressure vessel 8 is kept limited during start-up, whereby the required start-up torque and start-up current are also limited.
Once the drive has been sufficiently launched, the required start-up current drops and at that moment the blow-off valve 47 is closed, as a result of which the pressure vessel is no longer blown off and thus the compressor element 2 can suck open the inlet valve 7 as shown in Fig. 7 and begin to build up full pressure. the pressure boiler 8. This is referred to as a loaded operation.
If during the loaded operation of Figure 7 with the inlet valve 7 fully open, the pressure in the pressure vessel 8 rises too high, for example because there is less consumption from the consumer network, the compressor 1 is brought to an unloaded state.
For this purpose, the blow-off valve 47 is opened again, whereby the pressure is passed from the pressure vessel 8 to the intermediate chamber 41, whereby the valve element 25 is pushed upwards against the valve seat 23, while the piston remains sucked in its lower position by the reduced pressure on the underside 27 of the piston 24.
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As a result, the gas is vented from the pressure boiler 8
such assuch as displayeddisplayed with arrowwith arrow C inD in figurefigure 8 and8. partly fit in Will be balanced the inlet valve 7 something Open to go, Causing it gas flowing through route C blown off is going to be gets back
sucked in as with arrow C 'in figure 8 and / or via the bypass passage 44 as shown with arrow C.
As a result, the pressure in the pressure vessel 8 drops again, partly due to the fact that no fresh gas is sucked in and compressed by the closed inlet valve 7.
Due to the reduced pressure, during this phase of no-load running at a fixed speed, only a limited energy consumption is used to drive the compressor element 2.
However, the oil supply to the compressor element 2 must be continued for which a minimum pressure is required in the pressure vessel 8.
To this end, the inlet valve 7, in particular the blow-off outlet 42 and the bypass passage 44, are dimensioned such that, with the compressor element in unloaded operation with the inlet valve 7 and the blow-off valve 47 open, the pressure after stabilization of the regime is between 0.05 and 0.15 MPa.
To switch back from the unloaded state of Figure 8 to the loaded state, for example when there is again
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BE2017 / 5641 is used, all you have to do is close the blow-off valve with the drive 3 running.
The intermediate chamber 41 is thereby placed under atmospheric pressure via the connection 42-43 between the chamber 41 and the inlet 18 of the inlet valve 7.
The piston and the valve element are then sucked back down by turning the compressor element 2 to the state of Figure 5, whereby gas can be sucked in again and compressed.
To stop the compressor, it is first brought to the unloaded state as explained above by opening the blow-off valve 47, whereby the unloaded state of Figure 8 is achieved with the inlet valve 7 as good as closed, after which the drive 3 is stopped.
The compressor element 2 then stops rotating so that the pressure from the pressure vessel 8 via the compressor element 2 itself enters the inlet 4 and the inlet valve 7, also under the piston 24 and into the flow channel 20, while also in the intermediate chamber 41 the pressure of the pressure vessel 8 is present via the open blow-off valve 47.
Due to this pressure balance above and below the piston 24, the piston 24 is pushed upwards by the upward force of the spring 22 against the stop-forming collar 35 of the valve element 25 as shown in Fig. 9, so that the intermediate seal 40 of the sealing membrane 38 forms a seal between the piston 24 and the valve element 25.
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However, the pressure vessel 8 remains connected to the inlet 18 of the inlet valve 7 as indicated by arrow C in Figure 9, as a result of which the pressure in the pressure vessel 8 will gradually decrease.
Thanks to the intermediate seal 40, the combination of piston 24 and valve element 25 behaves in this situation as a non-return valve which prevents the gas and oil which has flowed back via the compressor element 2 itself to the inlet 4 of the compressor element 2 along the inlet filter 6 can escape, which without this check valve effect could cause gas to be vented together with oil via the inlet filter 6, which is of course not desirable.
In this case, therefore, no additional non-return valve is required as with the known compressors.
The operation of the combination 24-25 as a non-return valve is also important in the event of a breakdown in which the drive 3 has suddenly failed in the loaded state of the compressor 1, for example in the event of a belt break or a defect of the inverter in the event of a failure. a frequency controlled drive with variable speed.
Since the failure of the drive 3 occurs during a loaded operation, the blow-off valve 47 is closed at that moment and the inlet valve 7 is fully open as shown in Fig. 7.
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As a result of the compressor element 2 coming to a standstill, there is a risk that gas can escape to the environment together with oil via the inlet filter 6.
However, the pressure of the pressure vessel 8 settles via the compressor element 2 below the piston 24, while there is a low pressure above the piston 24 in the intermediate chamber 41 because of the closed blow-off valve 47.
Under the influence of the pressure under the piston 24 and the upward force of the spring 22, the piston 24 together with the valve element 25 is pushed upwards as a non-return valve against the valve seat 23 as shown in figure 10. This prevents, also in the event of failure of the drive 3, oil is blown out via the air filter 6.
When the failure of the actuator 3 is determined, the shut-off valve 47 can be opened to release the pressure in the pressure vessel as shown with arrow C in Fig. 11.
It is clear that in all circumstances the undesired discharge of oil via the air filter 6 is prevented thanks to the non-return valve action of the double valve 24-25.
Figure 12 shows an alternative inlet valve 7 which differs from the inlet valve of Figure 3 in that in this case the bypass passage 44 is located below the bottom 37 of the valve element 25, so that in this case the
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BE2017 / 5641 bypass passage 44 is directly connected to the intermediate chamber.
Such an inlet valve 7 can be used in an oil-injected compressor such as that of Fig. 1 but with a variable speed, and this to prevent the formation of condensate in the oil 14 at low temperatures of the oil as they may occur, for example, when passing over loaded with closed relief valve 47 to unloaded by controlling the speed of the compressor element 2 to a lower value.
In that case, when transferring to no-load, first the temperature of the oil is measured and when it threatens to drop below the condensing temperature, the compressor element 2 at the loaded speed will continue to temporarily drive and the blow-off valve 47 open as shown in figure 12.
In that case the inlet valve 7 remains partially open, whereby gas is sucked in and compressed as shown with arrow E in figure 12 while at the same time the pressure vessel 8 is blown off as shown with arrow F in figure 12.
Compression of the gas develops compression heat that is used to heat the oil up to when the temperature of the oil is higher than the condensing temperature.
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It is clear that in this case the condensate prevention can be controlled with only one single blow-off valve 47.
Figure 13 shows some examples of possible variants of inlet valves in which one is already better than the other in terms of opening without the dynamic flow rate creating the tendency for the valve element to be sucked shut again.
Embodiment a corresponds here to the inlet valve as described above with a valve element 25 with a flat head and a right-angled finish at the area of contact with the valve seat 23.
Surprisingly, such a valve element provides the best results, better for example than those of previously streamlined ball shape of the embodiment c from which one would expect better results, but which tends to be automatically sucked back again when sucking a gas through the compressor element 2. .
The embodiment e shows that it is also possible, for example, to use a hollow valve element 25 such as that of Fig. 3, but wherein the cavity of the valve element is left open and thus without the sealing membrane 38 covering the valve element 25.
When choosing the shape and dimensions of the head 34 of the valve element and of the zone of the housing 17 around the valve seat, it is important to choose it such that
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BE2017 / 5641 during the loaded operation of the compressor element 2 with the aforementioned relief valve 47 closed and the inlet valve open, due to the pressure difference between the static pressure at the inlet 18 of the inlet valve 7 and the static pressure in the intermediate chamber 41 the dynamic pressure drop due to the flow of the air drawn in along the valve seat ensures that a force is exerted on the valve element that is directed away from the valve seat 23.
The present invention is by no means limited to the embodiments described as examples and shown in the figures, but an inlet valve according to the invention and a compressor element and compressor equipped with it can be realized in all shapes and sizes without departing from the scope of the invention.

权利要求:
Claims (21)
[1]
Conclusions.
An inlet valve for the inlet of a compressor element of a compressor (1) provided with a pressure vessel (8) connected to the outlet (5) of the compressor element (2), the inlet valve (7) comprising a housing (17) with a external portion (17a) with an inlet (18) for the inlet valve (7) and an outlet (19) for the inlet valve (7) for connection to the inlet (4) of the compressor element (2) and an inner portion (17b) that together with the external part (17a) defines a flow channel (20) between the inlet (18) and the exit (19) of the inlet valve (7), said flow channel (20) being closable by means of a valve (21) which is pushed in a rest position by means of a spring (22) against a valve seat (23) of the inlet valve (7), characterized in that this valve (21) is composed of a piston (24) and a valve element (25) cooperating with it wherein the piston (24) is slidably arranged in axial direction (X-X ') in a guide (26) of the housing ng (17) and is pushed in the direction of the valve seat (23) by means of the aforementioned spring (22), the piston (24) on the side (27) remote from the valve seat (23) being connected to the outlet (11) of the inlet valve (7) and wherein the valve element (7) is on the other side of the piston (24) and is formed by a valve stem piston (33) and a head (34) provided on the valve stem piston (33) ), which valve stem piston (33) is coaxially slidably arranged in the piston (24) to a certain depth which is limited by a stop that
2017/5641
BE2017 / 5641 is such that in the rest position the valve element (25) is pushed against the valve seat by the piston (24) under the influence of the aforementioned spring (22), an intermediate chamber between the valve stem piston (33) and the piston (23) (41) is enclosed which is provided with at least one blow-off inlet (32) via which the intermediate chamber (41) can be put in fluid communication with the pressure vessel (8) and with at least one blow-off outlet (42) which forms a permanent fluid connection between the intermediate chamber (41) and the inlet (18) of the inlet valve (7), the valve stem piston (33) further including a bypass passage (44) communicating with the intermediate chamber (41) and opening into the side wall of the valve stem piston (33) either directly or indirectly via a blow-off outlet (42) from the intermediate chamber (41).
[2]
An inlet valve according to claim 1, characterized in that it is arranged such that the piston (24) and the valve element (25) with their axial direction (X-X ') are oriented vertically with the valve element (25) above the piston ( 24).
[3]
The inlet valve according to claim 1 or 2, characterized in that seals (30) are provided between the piston (24) and the guide (26) of the housing (17).
[4]
An inlet valve according to any one of the preceding claims, characterized in that the valve stem piston (33) is slidably mounted in the piston (24) with no sliding fit without the intervention of seals.
2017/5641
BE2017 / 5641
[5]
The inlet valve according to any one of the preceding claims, characterized in that the aforementioned spring (22) is the only spring of the inlet valve (7).
[6]
The inlet valve according to any one of the preceding claims, characterized in that the aforementioned stop is formed by the stop-forming collar (35) of a wider head (34) and by a stop-forming edge (36) of the piston (24) cooperating therewith.
[7]
The inlet valve according to claim 6, characterized in that it includes an intermediate seal (40) between the stop-forming collar (35) of the wider head (34) and the stop-forming edge (36) of the piston (24).
[8]
The inlet valve according to claim 6 or 7, characterized in that the head (34) of the valve element (25) on the contact zone with the valve seat (23) is provided with a head seal (39).
[9]
The inlet valve according to claims 7 and 8, characterized in that the head (34) of valve element (25) is covered with a sealing membrane (38) to form the intermediate seal (40) and the head seal (39).
[10]
The inlet valve according to claim 9, characterized in that the sealing membrane (38) is provided with a blow-off opening (43) which forms a fluid connection between said blow-out outlet (42) of the intermediate chamber (41) and the inlet (18) of the inlet valve (7).
2017/5641
BE2017 / 5641
[11]
The inlet valve according to one of the preceding claims, characterized in that the diameter (A) of the head (34) of the valve element (25) at the area of contact with the valve seat (23) is larger than the outside diameter (B ) of the valve stem piston (33) of the valve element (25).
[12]
12. - Compressor with a compressor element (2) and a pressure vessel (8) connected to the outlet (5) of the compressor element (2), characterized in that the compressor element (2) is provided with an inlet valve (7) according to one of the preceding claims, wherein said inlet valve (7) is in fluid communication via a blow-off line (46) having a blow-off valve (47) therein with at least one blow-off inlet (32) of the intermediate chamber (41) of the inlet valve (7) and wherein inlet valve (7), in particular the blow-off outlet (42) and the bypass passage (44) are dimensioned such that, with the compressor element (2) in unloaded operation, the inlet valve (7) is fully open and the blow-off valve (47) is open set to blow off the contents of the pressure vessel (8) via the inlet valve (7), the pressure in the pressure vessel (8) after stabilization of the regime is between 0.05 and 0.15 MPa.
[13]
Compressor according to claim 12, characterized in that the shape and dimensions of the head (34) of the inlet valve (7) and of the valve seat are chosen such that, during the loaded operation of the compressor element (2), the aforementioned relief valve (47) in the blow-off line (46) is closed and the inlet valve (7) is open to allow the compressor element to suck in gas via the inlet valve (7), the pressure difference between the static
2017/5641
BE2017 / 5641 pressure at the inlet (18) of the inlet valve (7) and static pressure in the intermediate chamber (41) of the inlet valve (7) provides a force on the valve element (25) that is directed away from the valve seat ( 23).
[14]
Compressor according to claim 13, characterized in that the valve element (25) is provided with a head (34) which has a right-angled edge in the area where this head (34) contacts the valve seat (23).
[15]
Compressor according to claim 13 or 14, characterized in that the head (34) of the valve element (25) is substantially cylindrical at one end, the end circumferential edge of this cylindrical end forming the zone with which the head (34) of the valve element (25) in the closed state of the inlet valve (7) comes into contact with the valve seat (23) of the housing (17) of the inlet valve (7).
[16]
Compressor according to claim 14 or 15, characterized in that the head end of the cylindrical end is flat and extends perpendicular to the axial direction (X-X ').
[17]
Compressor according to claim 16 and claim 9 or 10, characterized in that the head (34) of the valve element (25) is partially hollow and spanned by the aforementioned sealing membrane (38) which is provided with a blow-off opening (43).
2017/5641
BE2017 / 5641
[18]
Compressor according to one of claims 12 to 17, characterized in that the housing (17) of the inlet valve (7) is provided with a blow-off connection (45) for external connection of the above-mentioned blow-off line (46) with the blow-off valve arranged therein (47), which blow-off connection (45) debouches at the blow-off entrance (32) of the intermediate chamber (41) of the inlet valve (7) or at the location of an intermediate chamber (31) in communication with it.
[19]
Compressor according to one of claims 12 to 18, characterized in that it is a compressor (1) with a drive (3) of the compressor element (2) with a fixed speed and that the bypass passage (44) indirectly via a blow-off output (42) is in fluid communication with the intermediate chamber (41) of the inlet valve (7), the blow-off valve (47) being used as a control element for switching between the loaded and unloaded rotation of the compressor element (2) at the fixed speed of the drive (3).
[20]
Compressor according to one of claims 12 to 18, characterized in that it is an oil-injected compressor (1) with a drive (3) of the compressor element (2) with a variable speed and that the bypass passage (44) is directly in fluid communication stands with the intermediate chamber (41) of the inlet valve (7), the blow-off valve (47) being used as an operating element to prevent condensation in the oil by, in the event of a danger of condensation forming when changing from loaded to unloaded, the speed of rotation to one
2017/5641
BE2017 / 5641 unloaded speed, to continue to drive the compressor element (2) at a speed that is higher than the unloaded speed and at the same time to open the blow-off valve (47) until the danger of condensation has disappeared
[21]
Compressor according to claim 20, characterized in that the blow-off valve (47) is the only valve of the compressor (1) to be able to move from loaded to unloaded
10 and for condensate prevention.

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同族专利:

---

公开号 | 公开日

---

EP3642487B1|2021-02-24|

---

AU2018287548A1|2019-12-19|

---

CN209261826U|2019-08-16|

---

US20200173563A1|2020-06-04|

---

RU2738906C1|2020-12-18|

---

EP3642487A1|2020-04-29|

---

KR102339335B1|2021-12-14|

---

BR112019026921A2|2020-06-30|

---

US11131396B2|2021-09-28|

---

KR20200020790A|2020-02-26|

---

ES2871143T3|2021-10-28|

---

BE1025352A1|2019-01-29|

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法律状态:
2019-02-25| FG| Patent granted|Effective date: 20190205 |

优先权:

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申请号 | 申请日 | 专利标题

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US201762522871P| true| 2017-06-21|2017-06-21|

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US62522871|2017-06-21|AU2018287548A| AU2018287548A1|2017-06-21|2018-06-04|Inlet valve for the inlet of a compressor element and compressor and compressor element provided with such an inlet valve|

---

EP18734305.8A| EP3642487B1|2017-06-21|2018-06-04|Inlet valve for the inlet of a compressor element and compressor and compressor element provided with such an inlet valve|

---

US16/620,347| US11131396B2|2017-06-21|2018-06-04|Inlet valve for the inlet of a compressor element and compressor and compressor element equipped with it|

---

KR1020207000746A| KR102339335B1|2017-06-21|2018-06-04|an inlet valve for an inlet of a compressor element, the compressor element provided with the inlet valve and the compressor|

---

ES18734305T| ES2871143T3|2017-06-21|2018-06-04|Inlet valve for the inlet of a compressor and compressor element and the compressor element provided with such an inlet valve|

---

RU2020102013A| RU2738906C1|2017-06-21|2018-06-04|Inlet valve for inlet of compressor element, as well as compressor and compressor element provided with such inlet valve|

---

PCT/IB2018/053975| WO2018234910A1|2017-06-21|2018-06-04|Inlet valve for the inlet of a compressor element and compressor and compressor element provided with such an inlet valve|

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BR112019026921-5A| BR112019026921A2|2017-06-21|2018-06-04|inlet valve for the entry of a compressor element and compressor and compressor element equipped with the same|

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CN201810639998.8A| CN109098971B|2017-06-21|2018-06-21|Inlet valve and compressor|

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CN201820957423.6U| CN209261826U|2017-06-21|2018-06-21|Inlet valve and compressor|