EP3859158A1 - Compressor device - Google Patents
Compressor device Download PDFInfo
- Publication number
- EP3859158A1 EP3859158A1 EP21164419.0A EP21164419A EP3859158A1 EP 3859158 A1 EP3859158 A1 EP 3859158A1 EP 21164419 A EP21164419 A EP 21164419A EP 3859158 A1 EP3859158 A1 EP 3859158A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- channel
- inlet
- passive element
- compressors
- 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.)
- Withdrawn
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
- F04F5/46—Arrangements of nozzles
- F04F5/465—Arrangements of nozzles with supersonic flow
Definitions
- the present invention relates to a compressor device with at least one compressor with an inlet and an outlet.
- the invention concerns a compressor device with at least one compressor with an inlet and an outlet and a channel for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer downstream from the compressor.
- Such a compressor device can be used to compress air or another gas or mixture of gases for example, whereby this compressed gas can supply a compressed air installation or another consumer of compressed gas and/or compressed air for example.
- compressed air is stated hereinafter it must also be taken to mean other compressed gases and/or mixture of gases.
- the compressor device there is a pressure vessel between the compressor and the consumer(s) that acts as a buffer for compressed air to stabilise the pressure of the compressed air that is supplied to the consumers.
- a non-return valve is also provided between the compressor and the consumers that prevents compressed air from being able to flow back to the compressor from the pressure vessel when the compressor is not supplying any compressed air to this pressure vessel.
- Such a non-return valve generally comprises a valve disk that is pushed against a seat by means of a spring and the pressure in the pressure vessel, and thus makes a reverse flow of compressed air from the pressure vessel to the compressor impossible.
- a reverse speed higher than the maximum allowed reverse speed could lead to failure of the compressor, which could have adverse effects on the safety of the compressor device as it could lead to breakages which, in the worst case, could give rise to the breaking off of a part that is thrown out at high speed, which constitutes a risk for any bystanders.
- the scroll compressor having a suction chamber communicating with the compression chambers, a discharge chamber, an oil separation chamber separating lubricating oil from the refrigerant gas and communicating with the discharge chamber and a back pressure chamber provided in front of the movable scroll member.
- a possible additional measure can consist of providing a release valve that can open when the compressor is not operating to allow a proportion of the compressed air to escape from the installation via this valve, such that the reverse turning of the compressor can be limited.
- Another possible additional measure provides an inlet throttle or inlet vanes that automatically close when the compressor is not operating, such that too high a reverse speed of the compressor can be prevented.
- a disadvantage of such a release valve and such an inlet throttle or inlet vanes is that they must be actively controlled, i.e. they must be opened or closed at the appropriate time, which makes such facilities liable to failure such that these facilities consequently must satisfy strict safety standards, which affects the cost.
- directly driven compressors in other words compressors that are driven directly by the motor without the intervention of a gearbox, the braking effect of such a gearbox is absent, which increases the risk of breakage in the compressor.
- the purpose of the present invention is to provide a solution to one or more of the aforementioned and/or other disadvantages.
- the object of the present invention is a compressor device with at least one compressor with an inlet and an outlet and a channel for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer, whereby this compressor device is provided with a passive element that limits the backflow of the compressed gas from the consumer to the aforementioned inlet to a set maximum flow.
- the passive element comprises a sonic nozzle.
- An advantage is that such a passive element will be able to limit the speed of the compressor during reverse turning and will thereby be able to prevent damage or limit the risk thereof.
- 'Passive element' means an element that contains no moving parts which means that such an element has a much lower risk of failure than elements with moving and/or actively controlled components, such that less stringent safety requirements are imposed and the element and the entire device can be constructed more easily and cheaply.
- the device is provided with a non-return valve, which during normal operation prevents the backflow of the compressed gas to the inlet.
- the aforementioned passive element will ensure that the reverse turning of the compressor is limited in the event of failure of the non-return valve.
- the passive element comprises a restriction in the channel for the backflow of the compressed gas from the pressure vessel to the aforementioned inlet.
- Such a restriction has the advantage that it can be easily constructed and applied in different locations, such as for example at the level of the inlet and/or the outlet of the compressor.
- the aforementioned restriction in the channel forms the minimum cross-section of the channel that is smaller than the cross-section of the inlet and/or the outlet of the compressor.
- the set maximum flow is imposed by the maximum allowed speed for the reverse turning of the compressor.
- the maximum allowed speed for reverse turning is determined by the mechanical limits of the compressor, for example.
- the set maximum flow rate can be chosen such that the speed of the reverse turning of the compressor is limited to a speed that is less than the maximum allowed speed for reverse turning, such that during reverse turning any form of damage can be prevented.
- the compressor device 1 according to the invention shown in figure 1 comprises one compression stage 2 that comprises a compressor 3 with an inlet 4 and an outlet 5.
- the compressor 3 concerned is constructed in the form of a screw compressor, but the invention is not limited as such and the compressor 3 concerned can also be constructed in the form of another type of compressor such as a tooth compressor, a scroll compressor, a turbocompressor or another type of compressor. It goes without saying that that the invention is not limited to application with one compression stage, but can also be applied in compressor devices with a number of compression stages, as will be described further.
- the compressor device further comprises a channel 6 comprising an inlet channel 6a that is connected to the inlet 4 for channelling the gas flow drawn in by the compressor 3 and an outlet channel 6b that is connected to the outlet 5 for channelling the gas flow compressed by the compressor 3 to a consumer 7 of compressed air and/or to a pressure network or consumer network to which one or more consumers 7 are connected, such as for example pneumatic machines or appliances. It is possible that there is a pressure vessel between the compressor 3 and the consumer 7, whereby the compressed gas flow is first channelled to the pressure vessel via the outlet channel 6b before the compressed gas is supplied to the consumer 7.
- the inlet 4 of the compressor 3 is directly connected to the surrounding air via the inlet channel 6a to draw in the air to be compressed.
- the inlet 4 of the compressor 3 is connected to a source, reservoir or similar for any type of gas or mixture of gases.
- the inlet channel 6a contains an inlet filter that is not shown in the drawings.
- the compressor 3 consists of a screw compressor with a double rotor 8 that is affixed rotatably in a housing 9.
- the double rotor 8 is formed by two helical rotors 10a and 10b with lobes that mesh together, and which together with the housing 9 define a gas chamber 11 at the inlet 4, which upon the rotation of the rotors 10a and 10b moves from the inlet 4 to the outlet 5 and thereby becomes increasingly smaller so that the gas trapped in this gas chamber 11 is compressed.
- the shaft 12 of one of the two rotors 10b is coupled to drive means in the form of a motor 13 for driving the screw compressor 3.
- a cooler 14 is placed in the outlet channel 6b, for example in the form of a heat exchanger.
- a passive element 15 is placed in the aforementioned outlet channel 6b, in this case downstream from the compressor 3.
- a non-return valve 16 is also provided in the aforementioned outlet channel 6b that is configured such that it enables a flow from the compressor 2 to the pressure vessel and the consumer 7, but not in the reverse direction.
- such a non-return valve 16 comprises a valve disk 16a that is pushed against a seat 16c by means of a spring 16b when the pressure downstream from the non-return valve 16 is greater than the pressure upstream from the non-return valve 16.
- the invention is not limited as such, as the non-return valve 16 can also be constructed in other ways, for example whereby no spring is provided and the valve disk 16a is pushed against the seat 16c under the influence of gravity and/or under the influence of the pressure difference across this non-return valve 16, and more specifically because the pressure downstream from the non-return valve 16 is greater than the pressure upstream therefrom. It goes without saying that a construction of a non-return valve with a spring 16c can also make use of the aforementioned principles of gravity and/or pressure difference for the closing thereof.
- the passive element 15 can be constructed in different ways.
- Figure 2 shows a practical embodiment whereby the element 15 is constructed as a step-shaped restriction 17 in the opposite flow direction Q' in the direction from the outlet 5 to the inlet 4 and thus a widening in the forward flow direction Q from the inlet 4 to the outlet 5.
- cross-section A of the outlet channel 6b upstream from the restriction 17 is smaller than the cross-section B of the channel downstream from the restriction 17.
- cross-section of the channel is reduced at the level of the step-shaped restriction 17 in the direction from the outlet 5 to the inlet 4.
- the operation of the compressor device 1 is very simple and as follows.
- the compressor 3 is driven by the motor 13.
- the passive element 15 will hereby have no or as good as no appreciable effect on the compressed air that flows through in the forward direction.
- the compressed air Downstream from the compressor 3, the compressed air is cooled by means of the cooler 14 to ensure that the compressed air is cold enough before being supplied to the consumer 7.
- the non-return valve 16 is pushed open due to the pressure of the compressed air against the force of the spring 16b such that the compressed air can flow to the consumer 7 in the forward flow direction Q.
- the compressor 3 can be stopped such that the pressure downstream from the non-return valve 16 is greater than the pressure upstream therefrom. This pressure difference, together with the force of the spring 16b ensures that the valve disk 16a is pushed against the seat 16c. The non-return valve 16 is thus closed, which prevents compressed air flowing back from the consumer 7 through the compressor 3 to the inlet 4 in the reverse flow direction Q'.
- the presence of the passive element 15 prevents the compressed air from flowing back through the compressor 3 in the reverse flow direction Q' at too high a rate.
- the restriction may be dimensioned such that the saturation flow rate of the passive element 15 during a backflow from the outlet 5 to the inlet 4 is less than the maximum flow rate imposed by the maximum allowed speed for the reverse turning of the compressor 3.
- the passive element 15 must be dimensioned such that the total backflow resistance is large enough to limit the backflow rate such that the reverse turning speed of the compressor 3 is kept below a limit value.
- Figure 3 shows a variant of the compressor device 1 of figure 1 , whereby in this case two compression stages 2a and 2b are provided, each consisting of a compressor 3a, respectively 3b, whereby the compressors 3a and 3b are connected together in series by means of a channel section 6c, such that the first compressor 3a forms a low-pressure stage 2a, while the second compressor 3b forms a highpressure stage 2b.
- compressors 3a and 3b are directly driven turbocompressors.
- the passive element 15 is between the two compressors 3a and 3b in the channel section 6c, upstream from the second compressor 3b, whereby in this case a cooler 14 is also provided in the aforementioned channel section 6c, whereby in this case this cooler 14 acts as an 'in tercooler'.
- the passive element 15 it is also possible for the passive element 15 to be in the inlet channel 6a, upstream from the first compressor 3a, or for the passive element 15 to be in the outlet channel 6b, downstream from the second compressor 3b.
- the passive element 15 is constructed as a sonic nozzle 18 as shown in figure 4 , whereby the nozzle 18 is integrated in the channel section 6c whereby this channel section 6c has a constant cross-section C.
- the sonic nozzle 18 is formed by a nozzle whose flow cross-section gradually decreases in the forward flow direction towards the consumer 7 to a minimum cross-section D, which for a forward gas flow in the flow direction Q forms the outlet 19 of the nozzle and which opens out into a wider channel section 6c to the consumer 7.
- the sonic nozzle 18 causes a small pressure loss in the forward flow direction Q, but in the reverse flow direction Q' behaves as a step-shaped restriction 17 in the channel section 6c whereby the cross-section of this channel section 6c decreases suddenly.
- the design of the sonic nozzle 18 is such that the speed of a gas that flows through in the forward direction will accelerate, whereby the speed of sound can be reached at the level of the outlet 19 of the nozzle 18.
- the diameter of the minimum cross-section D at the outlet 19 of the sonic nozzle 18 is such that the maximum flow rate that can flow through the sonic nozzle 18 at the speed of sound in the forward direction is at least equal to the maximum flow rate that can flow through the compressors 3a and 3b in the forward direction.
- the nozzle 18 is designed such that the maximum flow rate that can flow back through it in the reverse flow direction is imposed by the maximum allowed speed for the reverse turning of the compressors 3a and 3b. After all, the sonic nozzle 18 will behave as a step-shaped restriction 17 in the cross-section of the channel section 6c to prevent or limit the reverse turning speed of the compressors 3a and 3b.
- the passive element 15 is constructed as a step-shaped restriction 17, as shown in figure 2 .
- a cooler can be provided at the outlet 5b of the second compressor 3b to cool the compressed air before the supply to the consumer 7, whereby this cooler thus acts as an aftercooler of the compressor device 1.
- FIGS 5 and 6 show two alternative embodiments of a compressor device 1 according to the invention, whereby in this case the compressor device 1 comprises two compressors 3a and 3b that are connected together in parallel. They can be screw compressors, directly driven turbocompressors or another suitable type of compressor, or any combination of different types of compressors.
- the compressors 3a and 3b are each placed in a parallel branch 6c', respectively 6c" of the channel 6, whereby the compressors 3a and 3b are connected via a common section of the inlet and outlet channel 6a and 6b, both downstream and upstream from the compressors 3a and 3b.
- the passive element 15 is provided in the common outlet channel 6b located downstream from the compressors 3a and 3b, and can be constructed as a step-shaped restriction 17 as shown in figure 2 , or as a sonic nozzle 18 as shown in figure 4 , or in the form of another type of passive element that is configured such that in a normal flow direction of the compressed air it causes no or practically no flow resistance, but in a reverse flow direction Q' provides such a resistance that the reverse turning speed of the compressors 3a and 3b is limited to a safe value.
- the passive element 15 is provided in the upstream common inlet channel 6a.
- compressors 3a and 3b will simultaneously compress the air drawn in instead of in subsequent stages, as shown in figure 3 .
- the drawn in gas originates from the same common inlet channel 6a.
- the passive element 15 will prevent both compressors 3a and 3b from reverse turning at too high a speed by limiting the flow rate of the gas flow that flows back via the outlet channel 6b to the parallel branches 6c' and 6c". This has the advantage that both compressors 3a and 3b can be protected by means of one passive element 15.
- each of the compressors 3a and 3b has a separate inlet channel 6a', respectively 6a", and that each of these inlet channels 6a' and 6a" is provided with a passive element 15a, respectively 15b, that limits the backflow rate through each of the compressors 3a and 3b in the event of a failure of the non-return valve 16.
- the passive elements 15a and 15b are placed in the outlet channel 6b', respectively 6b", downstream from the compressor 3a and 3b concerned.
- the first inlet channel 6a' draws in air while the inlet channel 6a" draws in another type of gas from a source, reservoir or similar.
- each passive element 15a and 15b will now each prevent the corresponding compressor 3a and 3b from turning again at too high a speed. This has the advantage that each passive element 15a and 15b can be adapted to the specific requirements of the corresponding compressor 3a, respectively 3b.
- compressor device 1 can hereby be provided with one or more coolers 14 or otherwise, between or after one or more of the compressors 3, 3a, 3b.
- the passive element 15 in all embodiments described above can be placed at different locations in the compressor device 1, and if desired can be in the inlet or outlet of a compressor 3, 3a, 3b or can be integrated in one of the compressor housings 9. This last one has the advantage that the passive element 15 does not have to be built into the channel 6a, 6b, 6c.
- the passive element 15 is integrated in a component of the compressor device 1, such as in the non-return valve 16 itself or in the cooler 14 or in the inlet filter or similar.
- non-return valve 16 can be replaced by movable inlet vanes, an adjustable inlet throttle and/or a release valve that is activated in order to divert the back flowing air to the environment before it can flow back through the compressor.
- the compressor device 1 can also be used to compress another gas or mixture of gases other than air.
- the restriction as shown in figure 2 does not need to be limited to one single step-shaped restriction 17, but can also comprise a number of successive step-shaped restrictions 17 or a gradual transition of diameter, in combination or otherwise with one or more step-shaped restrictions 17.
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Abstract
Description
- The present invention relates to a compressor device with at least one compressor with an inlet and an outlet.
- More specifically, the invention concerns a compressor device with at least one compressor with an inlet and an outlet and a channel for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer downstream from the compressor.
- Such a compressor device can be used to compress air or another gas or mixture of gases for example, whereby this compressed gas can supply a compressed air installation or another consumer of compressed gas and/or compressed air for example. When compressed air is stated hereinafter it must also be taken to mean other compressed gases and/or mixture of gases.
- Generally, according to the flow direction of the gas that flows through the compressor device, there is a pressure vessel between the compressor and the consumer(s) that acts as a buffer for compressed air to stabilise the pressure of the compressed air that is supplied to the consumers.
- Generally a non-return valve is also provided between the compressor and the consumers that prevents compressed air from being able to flow back to the compressor from the pressure vessel when the compressor is not supplying any compressed air to this pressure vessel.
- Such a non-return valve generally comprises a valve disk that is pushed against a seat by means of a spring and the pressure in the pressure vessel, and thus makes a reverse flow of compressed air from the pressure vessel to the compressor impossible.
- When such a non-return valve fails there is a risk that the backflow of compressed air is not prevented when the compressor is not supplying any compressed air to the pressure vessel, and that consequently the compressed air flows back in the opposite direction through the compressor to the inlet of the compressor. As a result, the energy present in the compressed air can ensure that the compressor is driven undesirably, according to the principle of a turbine, in the opposite direction to the normal direction of rotation.
- When the compressor turns backwards at high speed, this can have adverse effects on the components of the compressor. At a relatively low reverse speed there will only be limited adverse effects, if any, for example in the form of possible oil leaks that can occur around the seals for example.
- When the reverse speed becomes greater, mechanical damage can occur to the components of the compressor such as bearings and gearwheels for example, such that the efficiency can be detrimentally affected.
- A reverse speed higher than the maximum allowed reverse speed could lead to failure of the compressor, which could have adverse effects on the safety of the compressor device as it could lead to breakages which, in the worst case, could give rise to the breaking off of a part that is thrown out at high speed, which constitutes a risk for any bystanders.
- In order to curtail the dangers of the aforementioned risk, this is taken into account in the development and calculation of the compressor, which gives rise to more expensive and heavier constructions of compressors.
- One example can be found in
EP 2,131,040 A having Toyota Jidoshokki KK as applicant, whereby a scroll compressor is described. The scroll compressor having a suction chamber communicating with the compression chambers, a discharge chamber, an oil separation chamber separating lubricating oil from the refrigerant gas and communicating with the discharge chamber and a back pressure chamber provided in front of the movable scroll member. - In order to endeavour to prevent such adverse effects, other additional measures are also already known.
- A possible additional measure can consist of providing a release valve that can open when the compressor is not operating to allow a proportion of the compressed air to escape from the installation via this valve, such that the reverse turning of the compressor can be limited.
- Another possible additional measure provides an inlet throttle or inlet vanes that automatically close when the compressor is not operating, such that too high a reverse speed of the compressor can be prevented.
- A disadvantage of such a release valve and such an inlet throttle or inlet vanes is that they must be actively controlled, i.e. they must be opened or closed at the appropriate time, which makes such facilities liable to failure such that these facilities consequently must satisfy strict safety standards, which affects the cost.
- Most compressors are equipped with a gearbox that exerts something of a braking effect during the backflow of compressed air and the resulting reverse turning of the compressor and gearbox.
- This has a favourable effect on the aforementioned risk but has the additional adverse effect that the gearbox, when reverse turning, can be damaged around the seals or possible breakages can occur.
- With directly driven compressors, in other words compressors that are driven directly by the motor without the intervention of a gearbox, the braking effect of such a gearbox is absent, which increases the risk of breakage in the compressor.
- The purpose of the present invention is to provide a solution to one or more of the aforementioned and/or other disadvantages.
- To this end the object of the present invention is a compressor device with at least one compressor with an inlet and an outlet and a channel for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer, whereby this compressor device is provided with a passive element that limits the backflow of the compressed gas from the consumer to the aforementioned inlet to a set maximum flow. Optionally the passive element comprises a sonic nozzle.
- An advantage is that such a passive element will be able to limit the speed of the compressor during reverse turning and will thereby be able to prevent damage or limit the risk thereof.
- 'Passive element' means an element that contains no moving parts which means that such an element has a much lower risk of failure than elements with moving and/or actively controlled components, such that less stringent safety requirements are imposed and the element and the entire device can be constructed more easily and cheaply.
- It is possible, but not necessary, that the device is provided with a non-return valve, which during normal operation prevents the backflow of the compressed gas to the inlet. In this case the aforementioned passive element will ensure that the reverse turning of the compressor is limited in the event of failure of the non-return valve. Preferably the passive element comprises a restriction in the channel for the backflow of the compressed gas from the pressure vessel to the aforementioned inlet.
- Such a restriction has the advantage that it can be easily constructed and applied in different locations, such as for example at the level of the inlet and/or the outlet of the compressor.
- Preferably the aforementioned restriction in the channel forms the minimum cross-section of the channel that is smaller than the cross-section of the inlet and/or the outlet of the compressor.
- According to a preferred characteristic of the invention the set maximum flow is imposed by the maximum allowed speed for the reverse turning of the compressor.
- This has the advantage that during the reverse turning of the compressor the speed can never be higher than the maximum allowed speed such that serious damage to the compressor can be prevented.
- The maximum allowed speed for reverse turning is determined by the mechanical limits of the compressor, for example.
- It is not excluded that the set maximum flow rate can be chosen such that the speed of the reverse turning of the compressor is limited to a speed that is less than the maximum allowed speed for reverse turning, such that during reverse turning any form of damage can be prevented.
- With the intention of better showing the characteristics of the invention, a few preferred embodiments of a compressor device according to the invention are described hereinafter by way of an example, without any limiting nature, with reference to the accompanying drawings, wherein:
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figure 1 schematically shows a compressor device according to the invention; -
figure 2 shows a possible embodiment of the section indicated by F2 infigure 1 ; -
figure 3 schematically shows an alternative embodiment of a compressor device according to the invention; -
figure 4 shows a possible embodiment of the section indicated by F4 infigure 3 ; -
figures 5 and 6 schematically show alternative embodiments of a compressor device according to the invention. - The
compressor device 1 according to the invention shown infigure 1 comprises onecompression stage 2 that comprises acompressor 3 with an inlet 4 and an outlet 5. In this case thecompressor 3 concerned is constructed in the form of a screw compressor, but the invention is not limited as such and thecompressor 3 concerned can also be constructed in the form of another type of compressor such as a tooth compressor, a scroll compressor, a turbocompressor or another type of compressor. It goes without saying that that the invention is not limited to application with one compression stage, but can also be applied in compressor devices with a number of compression stages, as will be described further. - The compressor device further comprises a
channel 6 comprising aninlet channel 6a that is connected to the inlet 4 for channelling the gas flow drawn in by thecompressor 3 and anoutlet channel 6b that is connected to the outlet 5 for channelling the gas flow compressed by thecompressor 3 to aconsumer 7 of compressed air and/or to a pressure network or consumer network to which one ormore consumers 7 are connected, such as for example pneumatic machines or appliances. It is possible that there is a pressure vessel between thecompressor 3 and theconsumer 7, whereby the compressed gas flow is first channelled to the pressure vessel via theoutlet channel 6b before the compressed gas is supplied to theconsumer 7. - In this case the inlet 4 of the
compressor 3 is directly connected to the surrounding air via theinlet channel 6a to draw in the air to be compressed. However, it is not excluded that the inlet 4 of thecompressor 3 is connected to a source, reservoir or similar for any type of gas or mixture of gases. - Normally the
inlet channel 6a contains an inlet filter that is not shown in the drawings. - As stated, in this example the
compressor 3 consists of a screw compressor with a double rotor 8 that is affixed rotatably in ahousing 9. - The double rotor 8, as is known, is formed by two
helical rotors housing 9 define agas chamber 11 at the inlet 4, which upon the rotation of therotors gas chamber 11 is compressed. - The
shaft 12 of one of the tworotors 10b is coupled to drive means in the form of amotor 13 for driving thescrew compressor 3. - In this case, but not necessarily, a
cooler 14 is placed in theoutlet channel 6b, for example in the form of a heat exchanger. - According to the invention, a
passive element 15 is placed in theaforementioned outlet channel 6b, in this case downstream from thecompressor 3. Anon-return valve 16 is also provided in theaforementioned outlet channel 6b that is configured such that it enables a flow from thecompressor 2 to the pressure vessel and theconsumer 7, but not in the reverse direction. - In a preferred embodiment such a
non-return valve 16 comprises avalve disk 16a that is pushed against aseat 16c by means of aspring 16b when the pressure downstream from thenon-return valve 16 is greater than the pressure upstream from thenon-return valve 16. The invention is not limited as such, as thenon-return valve 16 can also be constructed in other ways, for example whereby no spring is provided and thevalve disk 16a is pushed against theseat 16c under the influence of gravity and/or under the influence of the pressure difference across thisnon-return valve 16, and more specifically because the pressure downstream from thenon-return valve 16 is greater than the pressure upstream therefrom. It goes without saying that a construction of a non-return valve with aspring 16c can also make use of the aforementioned principles of gravity and/or pressure difference for the closing thereof. - The
passive element 15 can be constructed in different ways.Figure 2 shows a practical embodiment whereby theelement 15 is constructed as a step-shaped restriction 17 in the opposite flow direction Q' in the direction from the outlet 5 to the inlet 4 and thus a widening in the forward flow direction Q from the inlet 4 to the outlet 5. - Hereby the cross-section A of the
outlet channel 6b upstream from therestriction 17 is smaller than the cross-section B of the channel downstream from therestriction 17. In other words the cross-section of the channel is reduced at the level of the step-shaped restriction 17 in the direction from the outlet 5 to the inlet 4. - The operation of the
compressor device 1 is very simple and as follows. - During normal operation, the
compressor 3 is driven by themotor 13. - Surrounding air for example is drawn in by the
compressor 3 that is compressed and supplied at a higher pressure, via thepassive element 15 and then thenon-return valve 16, to theconsumer 7 that is connected to thechannel 6. - Thereby, when flowing through the
passive element 15 the gas flow experiences a widening of theoutlet channel 6b from a cross-section A to a cross-section B. - The
passive element 15 will hereby have no or as good as no appreciable effect on the compressed air that flows through in the forward direction. - Downstream from the
compressor 3, the compressed air is cooled by means of the cooler 14 to ensure that the compressed air is cold enough before being supplied to theconsumer 7. - During this normal operation, the
non-return valve 16 is pushed open due to the pressure of the compressed air against the force of thespring 16b such that the compressed air can flow to theconsumer 7 in the forward flow direction Q. - When the
consumer 7 no longer needs a gas flow, thecompressor 3 can be stopped such that the pressure downstream from thenon-return valve 16 is greater than the pressure upstream therefrom. This pressure difference, together with the force of thespring 16b ensures that thevalve disk 16a is pushed against theseat 16c. Thenon-return valve 16 is thus closed, which prevents compressed air flowing back from theconsumer 7 through thecompressor 3 to the inlet 4 in the reverse flow direction Q'. - If the
non-return valve 16 fails, the backflow in the reverse flow direction Q' is no longer prevented by thisnon-return valve 16 and air inevitably flows from theconsumer 7 back to the inlet 4 through thecompressor 3. - The presence of the
passive element 15 prevents the compressed air from flowing back through thecompressor 3 in the reverse flow direction Q' at too high a rate. - Indeed, during the backflow the gas flow will experience a sudden cross-section reduction or narrowing of the
outlet channel 6b at the location of thepassive element 15. At this cross-section reduction or narrowing a saturation occurs as of a certain flow rate, whereby the narrowing will not allow more flow through than this specific saturation flow, which depends on the dimensions of therestriction 17. - The restriction may be dimensioned such that the saturation flow rate of the
passive element 15 during a backflow from the outlet 5 to the inlet 4 is less than the maximum flow rate imposed by the maximum allowed speed for the reverse turning of thecompressor 3. - As the backflow rate is determined by the total flow resistance in the total backflow path through the
passive element 15, theoutlet channel 6b, thecompressor 3 and theinlet channel 6a, thepassive element 15 must be dimensioned such that the total backflow resistance is large enough to limit the backflow rate such that the reverse turning speed of thecompressor 3 is kept below a limit value. - This will ensure that the speed with which the
compressor 3 turns in the reverse under the effect of this backflowing compressed air will be limited. As a result thecompressor 3 is protected against possible damage. -
Figure 3 shows a variant of thecompressor device 1 offigure 1 , whereby in this case twocompression stages compressors 3a and 3b are connected together in series by means of achannel section 6c, such that the first compressor 3a forms a low-pressure stage 2a, while thesecond compressor 3b forms ahighpressure stage 2b. - In this example the
compressors 3a and 3b are directly driven turbocompressors. - In this example the
passive element 15 is between the twocompressors 3a and 3b in thechannel section 6c, upstream from thesecond compressor 3b, whereby in this case a cooler 14 is also provided in theaforementioned channel section 6c, whereby in this case this cooler 14 acts as an 'in tercooler'. - According to the invention it is also possible for the
passive element 15 to be in theinlet channel 6a, upstream from the first compressor 3a, or for thepassive element 15 to be in theoutlet channel 6b, downstream from thesecond compressor 3b. - In this example the
passive element 15 is constructed as asonic nozzle 18 as shown infigure 4 , whereby thenozzle 18 is integrated in thechannel section 6c whereby thischannel section 6c has a constant cross-section C. - In this case, the
sonic nozzle 18 is formed by a nozzle whose flow cross-section gradually decreases in the forward flow direction towards theconsumer 7 to a minimum cross-section D, which for a forward gas flow in the flow direction Q forms theoutlet 19 of the nozzle and which opens out into awider channel section 6c to theconsumer 7. - The
sonic nozzle 18 causes a small pressure loss in the forward flow direction Q, but in the reverse flow direction Q' behaves as a step-shapedrestriction 17 in thechannel section 6c whereby the cross-section of thischannel section 6c decreases suddenly. - The design of the
sonic nozzle 18 is such that the speed of a gas that flows through in the forward direction will accelerate, whereby the speed of sound can be reached at the level of theoutlet 19 of thenozzle 18. The diameter of the minimum cross-section D at theoutlet 19 of thesonic nozzle 18 is such that the maximum flow rate that can flow through thesonic nozzle 18 at the speed of sound in the forward direction is at least equal to the maximum flow rate that can flow through thecompressors 3a and 3b in the forward direction. - In this case too, the
nozzle 18 is designed such that the maximum flow rate that can flow back through it in the reverse flow direction is imposed by the maximum allowed speed for the reverse turning of thecompressors 3a and 3b. After all, thesonic nozzle 18 will behave as a step-shapedrestriction 17 in the cross-section of thechannel section 6c to prevent or limit the reverse turning speed of thecompressors 3a and 3b. - It is not excluded that in this embodiment the
passive element 15 is constructed as a step-shapedrestriction 17, as shown infigure 2 . - It is further clear that a cooler can be provided at the
outlet 5b of thesecond compressor 3b to cool the compressed air before the supply to theconsumer 7, whereby this cooler thus acts as an aftercooler of thecompressor device 1. -
Figures 5 and 6 show two alternative embodiments of acompressor device 1 according to the invention, whereby in this case thecompressor device 1 comprises twocompressors 3a and 3b that are connected together in parallel. They can be screw compressors, directly driven turbocompressors or another suitable type of compressor, or any combination of different types of compressors. - In the case of
figure 5 thecompressors 3a and 3b are each placed in aparallel branch 6c', respectively 6c" of thechannel 6, whereby thecompressors 3a and 3b are connected via a common section of the inlet andoutlet channel compressors 3a and 3b. - In this example the
passive element 15 is provided in thecommon outlet channel 6b located downstream from thecompressors 3a and 3b, and can be constructed as a step-shapedrestriction 17 as shown infigure 2 , or as asonic nozzle 18 as shown infigure 4 , or in the form of another type of passive element that is configured such that in a normal flow direction of the compressed air it causes no or practically no flow resistance, but in a reverse flow direction Q' provides such a resistance that the reverse turning speed of thecompressors 3a and 3b is limited to a safe value. - According to the invention it is not excluded that the
passive element 15 is provided in the upstreamcommon inlet channel 6a. - The operation of the
compressor device 1, as shown infigure 5 , is analogous to the embodiments described above. - In this case the
compressors 3a and 3b will simultaneously compress the air drawn in instead of in subsequent stages, as shown infigure 3 . - In
figure 5 the drawn in gas originates from the samecommon inlet channel 6a. In the event of a backflow of the compressed air, thepassive element 15 will prevent bothcompressors 3a and 3b from reverse turning at too high a speed by limiting the flow rate of the gas flow that flows back via theoutlet channel 6b to theparallel branches 6c' and 6c". This has the advantage that bothcompressors 3a and 3b can be protected by means of onepassive element 15. - In the example of
figure 6 thecompressors 3a and 3b are also placed in parallel analogous tofigure 5 , with the difference that each of thecompressors 3a and 3b has aseparate inlet channel 6a', respectively 6a", and that each of theseinlet channels 6a' and 6a" is provided with a passive element 15a, respectively 15b, that limits the backflow rate through each of thecompressors 3a and 3b in the event of a failure of thenon-return valve 16. - In this case it is not excluded either that the passive elements 15a and 15b are placed in the
outlet channel 6b', respectively 6b", downstream from thecompressor 3a and 3b concerned. - The operation of the
compressor device 1, as shown infigure 6 , is analogous to the embodiment offigure 5 described above. - In this embodiment it is possible for example that the
first inlet channel 6a' draws in air while theinlet channel 6a" draws in another type of gas from a source, reservoir or similar. - The passive elements 15a and 15b will now each prevent the
corresponding compressor 3a and 3b from turning again at too high a speed. This has the advantage that each passive element 15a and 15b can be adapted to the specific requirements of the corresponding compressor 3a, respectively 3b. - It is clear that in all embodiments, as shown in
figures 1 ,3 ,5 and 6 , more than one or more than twocompressors compressors compressor device 1 can hereby be provided with one ormore coolers 14 or otherwise, between or after one or more of thecompressors - It is also clear that the invention can also be applied to all possible combinations of serial and parallel connected compressors. As a result a
passive element 15 can be provided per group of compressors and/or per individual compressor. - It is also clear that the
passive element 15 in all embodiments described above can be placed at different locations in thecompressor device 1, and if desired can be in the inlet or outlet of acompressor compressor housings 9. This last one has the advantage that thepassive element 15 does not have to be built into thechannel - It is not excluded either that the
passive element 15 is integrated in a component of thecompressor device 1, such as in thenon-return valve 16 itself or in the cooler 14 or in the inlet filter or similar. - Alternatively, the
non-return valve 16 can be replaced by movable inlet vanes, an adjustable inlet throttle and/or a release valve that is activated in order to divert the back flowing air to the environment before it can flow back through the compressor. - As already stated above, it is also clear that in all the examples described the
compressor device 1 can also be used to compress another gas or mixture of gases other than air. - The restriction as shown in
figure 2 does not need to be limited to one single step-shapedrestriction 17, but can also comprise a number of successive step-shapedrestrictions 17 or a gradual transition of diameter, in combination or otherwise with one or more step-shapedrestrictions 17. - The present invention is by no means limited to the embodiments described as an example and shown in the drawings, but a compressor device according to the invention can be realised in all kinds of forms and dimensions, without departing from the scope of the invention.
Claims (15)
- Compressor device with at least one compressor (3) with an inlet (4) and an outlet (5) and a channel (6) for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer, characterised in that the compressor device (1) is provided with a passive element (15) that limits the backflow of the compressed gas from the consumer (7) to the inlet (4) to a set maximum flow.
- Compressor device according to claim 1, characterised in that the passive element (15) comprises a restriction in the channel (6) for the backflow of the compressed gas from the consumer (7) to the inlet (4) .
- Compressor device according to claim 2, characterised in that the aforementioned restriction forms a step-shaped restriction (17) in the channel (6), in the direction from the outlet (5) to the inlet (4) .
- Compressor device according to one or more of the previous claims, characterised in that the passive element (15) comprises a sonic nozzle (18) .
- Compressor device according to claim 4, characterised in that the sonic nozzle (18) comprises a nozzle whose flow cross-section decreases in the direction towards the consumer (7) to a minimum cross-section (C) that forms the outlet (19) of the nozzle and which opens into a wider channel (6) towards the consumer (7) .
- Compressor device according to claim 5, characterised in that the aforementioned nozzle is provided in a section of the channel (6) with a constant cross-section.
- Compressor device according to one or more of the previous claims, characterised in that the set maximum flow rate is imposed by the maximum speed for the reverse turning of the compressor (3).
- Compressor device according to one or more of the previous claims, characterised in that the passive element
(15) is downstream from the compressor (3) in the channel (6) or in the outlet (5) of the compressor (3) . - Compressor device according to one or more of the claims 1 to 7, characterised in that the passive element (15) is upstream from the compressor (3) in the channel (6) or in the inlet (4) of the compressor (3) .
- Compressor device according to any one of the previous claims, characterised in that the device (1) is provided with a non-return valve (16) that prevents the backflow of the compressed gas to the inlet (4) during normal operation .
- Compressor device according to any one of the previous claims, characterised in that the device (1) is provided with a number of compressors (3a, 3b) that are connected in series to one another by means of the channel (6a, 6b, 6c) .
- Compressor device according to claim 11, characterised in that the passive element (15) is between two compressors
(3a, 3b). - Compressor device according to any one of the previous claims 1 to 12, characterised in that the device (1) is provided with a number of compressors (3a, 3b) that are connected in parallel to one another, by means of the channel (6a, 6b, 6c), to a common outlet section (6b) downstream from the compressors (3a, 3b) and/or a common inlet section (6a) upstream from the compressors (3a, 3b), whereby a passive element (15) is applied in an aforementioned common inlet section and/or outlet section (6a and/or 6b) .
- Compressor device according to any one of the previous claims 1 to 13, characterised in that the device (1) is provided with a number of compressors (3a, 3b) that are connected in parallel to one another by means of the channel (6a, 6b, 6c) whereby a passive element (15) is provided for each compressor (3a, 3b) .
- Compressor device according to any one of the previous claims, characterised in that the compressor (3) is a directly driven turbocompressor.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BE2013/0580A BE1021301B1 (en) | 2013-09-05 | 2013-09-05 | COMPRESSOR DEVICE |
PCT/BE2014/000042 WO2015031961A2 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP14776980.6A EP3042080B2 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP17165818.0A EP3214313B1 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
Related Parent Applications (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14776980.6A Division-Into EP3042080B2 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP14776980.6A Division EP3042080B2 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP17165818.0A Division EP3214313B1 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3859158A1 true EP3859158A1 (en) | 2021-08-04 |
Family
ID=49385059
Family Applications (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14776980.6A Active EP3042080B2 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP17165818.0A Active EP3214313B1 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP21164419.0A Withdrawn EP3859158A1 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
Family Applications Before (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14776980.6A Active EP3042080B2 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
EP17165818.0A Active EP3214313B1 (en) | 2013-09-05 | 2014-09-02 | Compressor device |
Country Status (5)
Country | Link |
---|---|
EP (3) | EP3042080B2 (en) |
BE (1) | BE1021301B1 (en) |
ES (2) | ES2741199T5 (en) |
TR (1) | TR201911182T4 (en) |
WO (1) | WO2015031961A2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11401934B2 (en) | 2017-01-31 | 2022-08-02 | Hitachi Industrial Equipment Systems Co., Ltd. | Rotary displacement compressor having a check valve and a backflow control valve arranged in series through a discharge pipe |
US11092363B2 (en) * | 2017-04-04 | 2021-08-17 | Danfoss A/S | Low back pressure flow limiter |
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- 2014-09-02 ES ES14776980T patent/ES2741199T5/en active Active
- 2014-09-02 EP EP17165818.0A patent/EP3214313B1/en active Active
- 2014-09-02 TR TR2019/11182T patent/TR201911182T4/en unknown
- 2014-09-02 EP EP21164419.0A patent/EP3859158A1/en not_active Withdrawn
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Also Published As
Publication number | Publication date |
---|---|
EP3042080A2 (en) | 2016-07-13 |
EP3214313A1 (en) | 2017-09-06 |
BE1021301B1 (en) | 2015-10-26 |
ES2741199T5 (en) | 2022-11-24 |
EP3214313B1 (en) | 2021-03-24 |
ES2741199T3 (en) | 2020-02-10 |
EP3042080B1 (en) | 2019-05-08 |
ES2874254T3 (en) | 2021-11-04 |
WO2015031961A2 (en) | 2015-03-12 |
TR201911182T4 (en) | 2019-08-21 |
EP3042080B2 (en) | 2022-08-10 |
WO2015031961A3 (en) | 2015-05-07 |
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