US20190203712A1 - System for an Utility Vehicle Comprising a Screw Compressor and an Electric Motor - Google Patents
System for an Utility Vehicle Comprising a Screw Compressor and an Electric Motor Download PDFInfo
- Publication number
- US20190203712A1 US20190203712A1 US16/297,148 US201916297148A US2019203712A1 US 20190203712 A1 US20190203712 A1 US 20190203712A1 US 201916297148 A US201916297148 A US 201916297148A US 2019203712 A1 US2019203712 A1 US 2019203712A1
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- United States
- Prior art keywords
- flange
- electric motor
- screw compressor
- oil
- cooling
- 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.)
- Abandoned
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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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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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
- F04C29/04—Heating; Cooling; Heat insulation
-
- 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
- F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
- F04C27/006—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type pumps, e.g. gear pumps
-
- 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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
-
- 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
- F04C2210/00—Fluid
- F04C2210/10—Fluid working
- F04C2210/1005—Air
-
- 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
- F04C2210/00—Fluid
- F04C2210/22—Fluid gaseous, i.e. compressible
- F04C2210/221—Air
-
- 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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- 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
- F04C2240/00—Components
- F04C2240/40—Electric motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/16—Air or water being indistinctly used as working fluid, i.e. the machine can work equally with air or water without any modification
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/20—Heat transfer, e.g. cooling
- F05B2260/211—Heat transfer, e.g. cooling by intercooling, e.g. during a compression cycle
- F05B2260/212—Heat transfer, e.g. cooling by intercooling, e.g. during a compression cycle by water injection
Definitions
- the present invention relates to a system for a utility vehicle, comprising a screw compressor and an electric motor.
- Screw compressors for utility vehicles are already known from the prior art. Such screw compressors are used to provide the compressed air required for, for example, the brake system of the utility vehicle.
- oil-filled compressors in particular also screw compressors
- screw compressors in the case of which it is necessary to regulate the oil temperature.
- an external oil cooler being provided which is connected to the oil-filled compressor and to the oil circuit via a thermostat valve.
- the oil cooler is a heat exchanger which has two mutually separate circuits, wherein the first circuit is provided for the hot liquid, that is to say the compressor oil, and the second circuit is provided for the cooling liquid.
- cooling liquid use may for example be made of air, water mixtures with an antifreeze, or another oil.
- This oil cooler must then be connected to the compressor oil circuit by way of pipes or hoses, and the oil circuit must be safeguarded against leakage.
- This external volume must furthermore be filled with oil, such that the total quantity of oil is also increased.
- the system inertia is thus increased.
- the oil cooler must be mechanically accommodated and fastened, either by use of brackets situated in the surroundings or by use of a separate bracket, which necessitates additional fastening means and also structural space.
- DE 37 17 493 A1 discloses a screw compressor installation which is arranged in a compact housing and which has an oil cooler on the electric motor of the screw compressor.
- DE 10 2010 015 151 A1 has disclosed a compressor flange for a screw compressor.
- US 2014/0190674 A1 has disclosed a connecting flange for a heat exchanger of a motor vehicle, which connecting flange has cooling channels.
- DE 10 2013 011 061 B3 has disclosed a heat exchanger having a flange connection, wherein the flange connection has a connecting flange which is a die-cast part and which has passage holes, produced by casting, for receiving threaded bolts.
- a system for a utility vehicle comprises a screw compressor and an electric motor, wherein the electric motor drives the screw compressor.
- the electric motor is connected to the screw compressor by way of a flange, wherein the flange has at least one cooling port, and wherein at least one cooling channel is provided in the flange.
- the invention is based on the underlying concept of creating a space-saving cooling facility by virtue of a connecting element, which is cooled, being provided between the screw compressor and electric motor. It is thus no longer necessary to provide air cooling of the electric motor and of the screw compressor. Rather, a cooling facility is created in a targeted fashion directly at the location at which with the greatest heat generation is present in the system.
- the drive shaft for the drive of the screw compressor by the electric motor may be guided in the flange.
- the heat generated there can thus be easily dissipated via the flange.
- the cooling fluid for the flange may be a water-based cooling fluid, in particular cooling water or a mixture of water and a further component, for example methylene glycol or some other suitable antifreeze.
- the screw compressor may be one which serves for the supply of compressed air to a pneumatic brake installation of a utility vehicle.
- the screw compressor may be one which serves for the supply of compressed air to a pneumatic brake installation of a utility vehicle.
- the electric motor may have an electric motor flange which is provided for the connection to the flange.
- the electric motor flange may be an electric motor flange of standard design of the electric motor. An adaptation is thus not necessary, which permits an inexpensive solution.
- the seal of the cooling channel may be realized for the first time in the assembled state as a result of the assembly of the electric motor flange and flange. In this way, it is easily realized that, in the assembled state of the system, the cooling fluid is intended to and can come into direct contact at least with parts of the electric motor flange.
- FIG. 1 is a schematic sectional illustration of an exemplary embodiment according to the invention for a system for a utility vehicle comprising a screw compressor and an electric motor.
- FIG. 2 is a perspective view of the system in the assembled state.
- FIGS. 3A, 3B are perspective views of the flange between the screw compressor and the electric motor.
- FIG. 1 shows, in a schematic sectional illustration, a screw compressor 10 in the context of an exemplary embodiment of the present invention.
- the screw compressor 10 has a fastening flange 12 for the mechanical fastening of the screw compressor 10 to an electric motor (not shown in any more detail here).
- the screw 18 meshes with the screw 16 and is driven by means of the latter.
- the screw compressor 10 has a housing 20 in which the main components of the screw compressor 10 are accommodated.
- the housing 20 is filled with oil 22 .
- an inlet connector 24 is provided on the housing 20 of the screw compressor 10 .
- the inlet connector 24 is in this case designed such that an air filter 26 is arranged at said inlet connector.
- an air inlet 28 is provided radially on the air inlet connector 24 .
- a spring-loaded valve insert 30 which is designed here as an axial seal.
- Said valve insert 30 serves as a check valve.
- an air feed channel 32 Downstream of the valve insert 30 , there is provided an air feed channel 32 which feeds the air to the two screws 16 , 18 .
- an air outlet pipe 34 with a riser line 36 .
- a temperature sensor 38 In the region of the end of the riser line 36 , there is provided a temperature sensor 38 by means of which the oil temperature can be monitored.
- a holder 40 for an air deoiling element 42 is also provided in the air outlet region.
- the holder 40 for the air deoiling element has the air deoiling element 42 in the region facing toward the base (as also shown in FIG. 1 ).
- a corresponding filter screen or known filter and oil separating devices 44 is also provided, in the interior of the air deoiling element 42 , which will not be specified in any more detail.
- the holder 40 for the air deoiling element 42 has an air outlet opening 46 which leads to a check valve 48 and a minimum pressure valve 50 .
- the check valve 48 and the minimum pressure valve 50 may also be formed in one common combined valve.
- the air outlet 51 is provided downstream of the check valve 48 .
- the air outlet 51 is generally connected to correspondingly known compressed-air consumers.
- a riser line 52 is provided which has a filter and check valve 54 at the outlet of the holder 40 for the air deoiling element 42 at the transition into the housing 20 .
- a nozzle 56 is provided, downstream of the filter and check valve 54 , in a housing bore.
- the oil return line 58 leads back into approximately the central region of the screw 16 or of the screw 18 in order to feed oil 22 thereto again.
- An oil drain screw 59 is provided in the base region, in the assembled state, of the housing 20 .
- a corresponding oil outflow opening can be opened, via which the oil 22 can be drained.
- the attachment piece 60 to which the oil filter 62 is fastened. Via an oil filter inlet channel 64 , which is arranged in the housing 20 , the oil 22 is conducted firstly to a thermostat valve 66 .
- thermostat valve 66 it is possible for an open-loop and/or closed-loop control device to be provided by means of which the oil temperature of the oil 22 situated in the housing 20 can be monitored and set to a setpoint value.
- the cooler 74 is connected to the attachment piece 60 .
- a safety valve 76 In the upper region of the housing 20 (in relation to the assembled state), there is situated a safety valve 76 , by means of which an excessively high pressure in the housing 20 can be dissipated.
- a bypass line 78 which leads to a relief valve 80 .
- a relief valve 80 which is activated by means of a connection to the air feed 32 , air can be returned into the region of the air inlet 28 .
- a ventilation valve not shown in any more detail
- a nozzle nozzle
- an oil level sensor 82 may be provided in the outer wall of the housing 20 .
- Said oil level sensor 82 may for example be an optical sensor, and may be designed and configured such that, on the basis of the sensor signal, it can be identified whether the oil level during operation is above the oil level sensor 82 or whether the oil level sensor 82 is exposed, and thus the oil level has correspondingly fallen.
- an alarm unit which outputs or transmits a corresponding error message or warning message to the user of the system.
- the function of the screw compressor 10 shown in FIG. 1 is as follows.
- Air is fed via the air inlet 28 and passes via the check valve 30 to the screws 16 , 18 , where the air is compressed.
- the compressed air-oil mixture which, having been compressed by a factor of between 5 and 16 downstream of the screws 16 and 18 , rises through the outlet line 34 via the riser pipe 36 , is blown directly onto the temperature sensor 38 .
- the air which still partially carries oil particles, is then conducted via the holder 40 into the air deoiling element 42 and, if the corresponding minimum pressure is attained, passes into the air outlet line 51 .
- the oil 22 situated in the housing 20 is kept at operating temperature via the oil filter 62 and possibly via the heat exchanger 74 .
- the heat exchanger 74 is not used and is also not activated.
- the corresponding activation is performed by means of the thermostat valve 66 .
- oil is fed via the line 68 to the screw 18 or to the screw 16 , and also to the bearing 70 .
- the screw 16 or the screw 18 is supplied with oil 22 via the return line 52 , 58 , and the purification of the oil 22 takes place here in the air deoiling element 42 .
- the relief valve 80 (not shown in any more detail), it is ensured that the high pressure that prevails for example at the outlet side of the screws 16 , 18 in the operational state cannot be enclosed in the region of the feed line 32 , and that, instead, in particular during the start-up of the compressor, there is always a low inlet pressure, in particular atmospheric pressure, prevailing in the region of the feed line 32 . Otherwise, upon a start-up of the compressor, a very high pressure would initially be generated at the outlet side of the screws 16 and 18 , which would overload the drive motor.
- FIG. 2 shows, in a perspective view, a view of an exemplary embodiment according to the invention of the overall system 1 with the electric motor 5 and the screw compressor 10 .
- FIG. 3A and FIG. 3B show perspective views of the flange 12 between screw compressor 10 and electric motor 5 .
- the flange 12 is situated in the middle as connecting part between screw compressor 10 and electric motor 5 .
- the flange 12 is formed as a separate component which is arranged between the screw compressor 10 and the electric motor 5 .
- the drive shaft 14 is guided through the central opening 100 of the flange 12 .
- the flange 12 has a cooling channel 102 .
- the cooling channel 102 of the flange 12 is, in this case and as can also be seen in the detail in FIG. 3A , open in the direction of the electric motor flange with regard to the assembled arrangement.
- the seal of the cooling channel 102 is formed for the first time in the assembled state as a result of the assembly of the electric motor flange and the flange 12 .
- the electric motor 5 and the electric motor flange have no cooling channel and no coolant ports.
- the coolant of the cooling system of the screw compressor 10 As is also shown in FIG. 2 , use is generally made of the coolant of the cooling system of the screw compressor 10 .
- the coolant circulates via the cooling channel 102 (cf. FIG. 3A ) in the flange 12 and is conducted to the oil cooler 74 via a rubber hose 108 connected to the cooling ports 104 , 106 .
- the cooling liquid After the cooling of the oil, the cooling liquid returns to the vehicle cooling circuit (not shown in any more detail) and, via this, is correspondingly connected via the cooling outlet port 110 .
Abstract
Description
- This application is a continuation of PCT International Application No. PCT/EP2017/073537, filed Sep. 19, 2017, which claims priority under 35 U.S.C. § 119 from German Patent Application No. 10 2016 011 442.8, filed Sep. 21, 2016, the entire disclosures of which are herein expressly incorporated by reference.
- The present invention relates to a system for a utility vehicle, comprising a screw compressor and an electric motor.
- Screw compressors for utility vehicles are already known from the prior art. Such screw compressors are used to provide the compressed air required for, for example, the brake system of the utility vehicle.
- In this context, in particular oil-filled compressors, in particular also screw compressors, are known, in the case of which it is necessary to regulate the oil temperature. This is generally realized by virtue of an external oil cooler being provided which is connected to the oil-filled compressor and to the oil circuit via a thermostat valve. Here, the oil cooler is a heat exchanger which has two mutually separate circuits, wherein the first circuit is provided for the hot liquid, that is to say the compressor oil, and the second circuit is provided for the cooling liquid. As cooling liquid, use may for example be made of air, water mixtures with an antifreeze, or another oil.
- This oil cooler must then be connected to the compressor oil circuit by way of pipes or hoses, and the oil circuit must be safeguarded against leakage.
- This external volume must furthermore be filled with oil, such that the total quantity of oil is also increased. The system inertia is thus increased. Furthermore, the oil cooler must be mechanically accommodated and fastened, either by use of brackets situated in the surroundings or by use of a separate bracket, which necessitates additional fastening means and also structural space.
- U.S. Pat. No. 4,780,061 has already disclosed a screw compressor with an integrated oil cooling arrangement.
- Furthermore, DE 37 17 493 A1 discloses a screw compressor installation which is arranged in a compact housing and which has an oil cooler on the electric motor of the screw compressor.
- DE 10 2010 015 151 A1 has disclosed a compressor flange for a screw compressor.
- Furthermore, US 2014/0190674 A1 has disclosed a connecting flange for a heat exchanger of a motor vehicle, which connecting flange has cooling channels.
- Furthermore, DE 10 2013 011 061 B3 has disclosed a heat exchanger having a flange connection, wherein the flange connection has a connecting flange which is a die-cast part and which has passage holes, produced by casting, for receiving threaded bolts.
- It is the object of the present invention to advantageously further develop a system for a utility vehicle, comprising a screw compressor and an electric motor, in particular such that a space-saving cooling facility for a generic system can be provided.
- According to the invention, a system for a utility vehicle comprises a screw compressor and an electric motor, wherein the electric motor drives the screw compressor. The electric motor is connected to the screw compressor by way of a flange, wherein the flange has at least one cooling port, and wherein at least one cooling channel is provided in the flange.
- The invention is based on the underlying concept of creating a space-saving cooling facility by virtue of a connecting element, which is cooled, being provided between the screw compressor and electric motor. It is thus no longer necessary to provide air cooling of the electric motor and of the screw compressor. Rather, a cooling facility is created in a targeted fashion directly at the location at which with the greatest heat generation is present in the system. By means of the arrangement of the flange between the electric motor and screw compressor, and owing to the fact that at least one cooling channel is provided in the flange, cooling using a suitable cooling fluid can be made possible.
- Provision may be made in particular for the flange to be a separate component. It is thus made possible for corresponding cooling channel geometries to be able to be easily provided in the flange. Both the screw compressor and the electric motor may in this case be, or remain, of a standard design with regard to the mechanical interface, that is to say the corresponding flanges, and require no modification.
- The drive shaft for the drive of the screw compressor by the electric motor may be guided in the flange. The heat generated there can thus be easily dissipated via the flange.
- The cooling fluid for the flange may be a water-based cooling fluid, in particular cooling water or a mixture of water and a further component, for example methylene glycol or some other suitable antifreeze.
- Provision may furthermore be made for the screw compressor to serve for generating compressed air. In particular, the screw compressor may be one which serves for the supply of compressed air to a pneumatic brake installation of a utility vehicle. Through the provision of a screw compressor with an electric motor, it is made possible for such a system to be permitted in the hybrid vehicle in the utility vehicle sector. A highly efficient system can be provided.
- The electric motor may have an electric motor flange which is provided for the connection to the flange. Here, the electric motor flange may be an electric motor flange of standard design of the electric motor. An adaptation is thus not necessary, which permits an inexpensive solution.
- Provision may be made in particular for the cooling channel of the flange to be open in the direction of the electric motor flange in the assembled state. In this way, direct contact of the cooling fluid with at least the part of the electric motor flange is made possible. In this way, an efficient dissipation of heat from the electric motor via the electric motor flange and the cooling fluid in the cooling channel of the flange can be made possible.
- The seal of the cooling channel may be realized for the first time in the assembled state as a result of the assembly of the electric motor flange and flange. In this way, it is easily realized that, in the assembled state of the system, the cooling fluid is intended to and can come into direct contact at least with parts of the electric motor flange.
- In particular, provision may furthermore be made for the electric motor to have no separate cooling channel and/or coolant ports. It is hereby ensured that the electric motor requires no special adaptations, which permits inexpensive production and assembly of the system.
- Other objects, advantages and novel features of the present invention will become apparent from the following detailed description of one or more preferred embodiments when considered in conjunction with the accompanying drawings.
-
FIG. 1 is a schematic sectional illustration of an exemplary embodiment according to the invention for a system for a utility vehicle comprising a screw compressor and an electric motor. -
FIG. 2 is a perspective view of the system in the assembled state. -
FIGS. 3A, 3B are perspective views of the flange between the screw compressor and the electric motor. -
FIG. 1 shows, in a schematic sectional illustration, ascrew compressor 10 in the context of an exemplary embodiment of the present invention. - The
screw compressor 10 has afastening flange 12 for the mechanical fastening of thescrew compressor 10 to an electric motor (not shown in any more detail here). - What is shown, however, is the
input shaft 14, by which the torque from the electric motor is transmitted to one of the twoscrews screw 16. - The
screw 18 meshes with thescrew 16 and is driven by means of the latter. - The
screw compressor 10 has ahousing 20 in which the main components of thescrew compressor 10 are accommodated. - The
housing 20 is filled withoil 22. - At the air inlet side, an
inlet connector 24 is provided on thehousing 20 of thescrew compressor 10. Theinlet connector 24 is in this case designed such that anair filter 26 is arranged at said inlet connector. Furthermore, anair inlet 28 is provided radially on theair inlet connector 24. - In the region between the
inlet connector 24 and the point at which theinlet connector 24 joins to thehousing 20, there is provided a spring-loadedvalve insert 30, which is designed here as an axial seal. - Said
valve insert 30 serves as a check valve. - Downstream of the
valve insert 30, there is provided anair feed channel 32 which feeds the air to the twoscrews - At the outlet side of the two
screws air outlet pipe 34 with ariser line 36. - In the region of the end of the
riser line 36, there is provided atemperature sensor 38 by means of which the oil temperature can be monitored. - Also provided in the air outlet region is a
holder 40 for anair deoiling element 42. - In the assembled state, the
holder 40 for the air deoiling element has theair deoiling element 42 in the region facing toward the base (as also shown inFIG. 1 ). - Also provided, in the interior of the
air deoiling element 42, is a corresponding filter screen or known filter andoil separating devices 44, which will not be specified in any more detail. - In the central upper region in relation to the assembled and operationally ready state (that is to say as shown in
FIG. 1 ), theholder 40 for theair deoiling element 42 has an air outlet opening 46 which leads to acheck valve 48 and aminimum pressure valve 50. Thecheck valve 48 and theminimum pressure valve 50 may also be formed in one common combined valve. - The
air outlet 51 is provided downstream of thecheck valve 48. - The
air outlet 51 is generally connected to correspondingly known compressed-air consumers. - In order for the
oil 22 that is situated and separated off in theair deoiling element 42 to be returned again into thehousing 20, ariser line 52 is provided which has a filter andcheck valve 54 at the outlet of theholder 40 for theair deoiling element 42 at the transition into thehousing 20. - A
nozzle 56 is provided, downstream of the filter andcheck valve 54, in a housing bore. Theoil return line 58 leads back into approximately the central region of thescrew 16 or of thescrew 18 in order to feedoil 22 thereto again. - An
oil drain screw 59 is provided in the base region, in the assembled state, of thehousing 20. By means of theoil drain screw 59, a corresponding oil outflow opening can be opened, via which theoil 22 can be drained. - Also provided in the lower region of the
housing 20 is theattachment piece 60 to which theoil filter 62 is fastened. Via an oilfilter inlet channel 64, which is arranged in thehousing 20, theoil 22 is conducted firstly to athermostat valve 66. - Instead of the
thermostat valve 66, it is possible for an open-loop and/or closed-loop control device to be provided by means of which the oil temperature of theoil 22 situated in thehousing 20 can be monitored and set to a setpoint value. - Downstream of the
thermostat valve 66, there is then the oil inlet of theoil filter 62, which, via acentral return line 68, conducts theoil 22 back to thescrew 18 or to thescrew 16 again, and also to the oil-lubricatedbearing 70 of theshaft 14. Also provided in the region of thebearing 70 is anozzle 72, which is provided in thehousing 20 in conjunction with thereturn line 68. - The cooler 74 is connected to the
attachment piece 60. - In the upper region of the housing 20 (in relation to the assembled state), there is situated a
safety valve 76, by means of which an excessively high pressure in thehousing 20 can be dissipated. - Upstream of the
minimum pressure valve 50, there is situated abypass line 78, which leads to arelief valve 80. Via saidrelief valve 80, which is activated by means of a connection to theair feed 32, air can be returned into the region of theair inlet 28. In this region, there may be provided a ventilation valve (not shown in any more detail) and also a nozzle (diameter constriction of the feeding line). - Furthermore, approximately at the level of the
line 34, anoil level sensor 82 may be provided in the outer wall of thehousing 20. Saidoil level sensor 82 may for example be an optical sensor, and may be designed and configured such that, on the basis of the sensor signal, it can be identified whether the oil level during operation is above theoil level sensor 82 or whether theoil level sensor 82 is exposed, and thus the oil level has correspondingly fallen. - In conjunction with this monitoring, it is also possible for an alarm unit to be provided which outputs or transmits a corresponding error message or warning message to the user of the system.
- The function of the
screw compressor 10 shown inFIG. 1 is as follows. - Air is fed via the
air inlet 28 and passes via thecheck valve 30 to thescrews screws outlet line 34 via theriser pipe 36, is blown directly onto thetemperature sensor 38. - The air, which still partially carries oil particles, is then conducted via the
holder 40 into theair deoiling element 42 and, if the corresponding minimum pressure is attained, passes into theair outlet line 51. - The
oil 22 situated in thehousing 20 is kept at operating temperature via theoil filter 62 and possibly via theheat exchanger 74. - If no cooling is necessary, the
heat exchanger 74 is not used and is also not activated. - The corresponding activation is performed by means of the
thermostat valve 66. After purification in theoil filter 64, oil is fed via theline 68 to thescrew 18 or to thescrew 16, and also to thebearing 70. Thescrew 16 or thescrew 18 is supplied withoil 22 via thereturn line oil 22 takes place here in theair deoiling element 42. - By means of the electric motor (not shown in any more detail), which transmits its torque via the
shaft 14 to thescrew 16, which in turn meshes with thescrew 18, thescrews screw compressor 10 are driven. - By means of the relief valve 80 (not shown in any more detail), it is ensured that the high pressure that prevails for example at the outlet side of the
screws feed line 32, and that, instead, in particular during the start-up of the compressor, there is always a low inlet pressure, in particular atmospheric pressure, prevailing in the region of thefeed line 32. Otherwise, upon a start-up of the compressor, a very high pressure would initially be generated at the outlet side of thescrews -
FIG. 2 shows, in a perspective view, a view of an exemplary embodiment according to the invention of theoverall system 1 with the electric motor 5 and thescrew compressor 10. -
FIG. 3A andFIG. 3B show perspective views of theflange 12 betweenscrew compressor 10 and electric motor 5. - The
flange 12 is situated in the middle as connecting part betweenscrew compressor 10 and electric motor 5. - Here, the
flange 12 is formed as a separate component which is arranged between thescrew compressor 10 and the electric motor 5. - Here, the
drive shaft 14 is guided through thecentral opening 100 of theflange 12. - The
flange 12 has acooling channel 102. - The cooling
channel 102 of theflange 12 is, in this case and as can also be seen in the detail inFIG. 3A , open in the direction of the electric motor flange with regard to the assembled arrangement. - The seal of the
cooling channel 102 is formed for the first time in the assembled state as a result of the assembly of the electric motor flange and theflange 12. - The electric motor 5 and the electric motor flange have no cooling channel and no coolant ports.
- As is also shown in
FIG. 2 , use is generally made of the coolant of the cooling system of thescrew compressor 10. The coolant circulates via the cooling channel 102 (cf.FIG. 3A ) in theflange 12 and is conducted to theoil cooler 74 via arubber hose 108 connected to the coolingports - After the cooling of the oil, the cooling liquid returns to the vehicle cooling circuit (not shown in any more detail) and, via this, is correspondingly connected via the
cooling outlet port 110. -
- 1 System
- 5 Electric motor
- 10 Screw compressor
- 12 Fastening flange
- 14 Input shaft
- 16 Screws
- 18 Screws
- 20 Housing
- 22 Oil
- 24 Inlet connector
- 26 Air filter
- 28 Air inlet
- 30 Valve insert
- 32 Air feed channel
- 34 Air outlet pipe
- 36 Riser line
- 38 Temperature sensor
- 40 Holder for an air deoiling element
- 42 Air deoiling element
- 44 Filter screen or known filter or oil separation devices
- 46 Air outlet opening
- 48 Check valve
- 50 Minimum pressure valve
- 51 Air outlet
- 52 Riser line
- 54 Filter and check valve
- 56 Nozzle
- 58 Oil return line
- 59 Oil drain screw
- 60 Attachment piece
- 60 a Outer ring
- 60 b Inner ring
- 62 Oil filter
- 64 Oil filter inlet channel
- 66 Thermostat valve
- 68 Return line
- 70 Bearing
- 72 Nozzle
- 74 Cooler, heat exchanger
- 76 Safety valve
- 78 Bypass line
- 80 Relief valve
- 82 Oil level sensor
- 100 Central opening
- 102 Cooling channel
- 104 Cooling ports
- 106 Cooling ports
- 108 Rubber hoses
- 110 Cooling outlet port
- The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.
Claims (10)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016011442.8A DE102016011442A1 (en) | 2016-09-21 | 2016-09-21 | System for a commercial vehicle comprising a screw compressor and an electric motor |
DE102016011442.8 | 2016-09-21 | ||
PCT/EP2017/073537 WO2018054855A1 (en) | 2016-09-21 | 2017-09-19 | System for an utility vehicle comprising a screw compressor and an electric motor |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2017/073537 Continuation WO2018054855A1 (en) | 2016-09-21 | 2017-09-19 | System for an utility vehicle comprising a screw compressor and an electric motor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20190203712A1 true US20190203712A1 (en) | 2019-07-04 |
Family
ID=60037545
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/297,148 Abandoned US20190203712A1 (en) | 2016-09-21 | 2019-03-08 | System for an Utility Vehicle Comprising a Screw Compressor and an Electric Motor |
Country Status (8)
Country | Link |
---|---|
US (1) | US20190203712A1 (en) |
EP (1) | EP3516227A1 (en) |
JP (1) | JP6835974B2 (en) |
KR (1) | KR102267530B1 (en) |
CN (1) | CN109790838B (en) |
BR (1) | BR112019005066A2 (en) |
DE (1) | DE102016011442A1 (en) |
WO (1) | WO2018054855A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN114738279A (en) * | 2022-03-26 | 2022-07-12 | 上海坤彧节能科技有限公司 | Double-stage compression main machine with interstage cooling device |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE1028274B1 (en) | 2020-05-07 | 2021-12-07 | Atlas Copco Airpower Nv | Compressor element with improved oil injector |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS4842405A (en) * | 1971-10-05 | 1973-06-20 | ||
JPS61152991A (en) * | 1984-12-26 | 1986-07-11 | Hitachi Ltd | Screw fluid machine |
US4748873A (en) | 1986-05-23 | 1988-06-07 | Raymond Engineering Inc. | Power wrench |
US4780061A (en) | 1987-08-06 | 1988-10-25 | American Standard Inc. | Screw compressor with integral oil cooling |
JPH01108380U (en) * | 1988-01-11 | 1989-07-21 | ||
CA2316822A1 (en) * | 1997-12-30 | 1999-07-15 | Ateliers Busch S.A. | Cooling device |
JP3668616B2 (en) * | 1998-09-17 | 2005-07-06 | 株式会社日立産機システム | Oil-free screw compressor |
JP4403670B2 (en) * | 2001-05-16 | 2010-01-27 | 株式会社デンソー | compressor |
DE102004060417B4 (en) * | 2004-12-14 | 2006-10-26 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compact screw compressor for mobile use in a vehicle |
JP4804927B2 (en) * | 2006-01-17 | 2011-11-02 | 株式会社神戸製鋼所 | Screw compressor |
JP4741992B2 (en) * | 2006-07-19 | 2011-08-10 | 株式会社日立産機システム | Oil-free screw compressor |
DE102007042318B4 (en) * | 2007-09-06 | 2017-11-30 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Compact dry running piston compressor |
JP5489825B2 (en) * | 2010-02-10 | 2014-05-14 | ナブテスコ株式会社 | Air compressor for railway vehicles |
TWI397483B (en) * | 2010-01-26 | 2013-06-01 | Nabtesco Corp | Air compression apparatus for railroad vehicle |
DE102010015151A1 (en) | 2010-04-16 | 2011-10-20 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compressor flange for screw compressors |
FR2978237B1 (en) | 2011-07-21 | 2013-12-20 | Valeo Systemes Thermiques | CONNECTING FLANGE, COLLECTOR BOX AND THERMAL EXCHANGER |
DE102013011061B3 (en) | 2013-07-02 | 2014-10-09 | Modine Manufacturing Company | Heat exchanger with a flange connection |
EP3263903B1 (en) * | 2015-02-25 | 2020-11-04 | Hitachi Industrial Equipment Systems Co., Ltd. | Oilless compressor |
-
2016
- 2016-09-21 DE DE102016011442.8A patent/DE102016011442A1/en not_active Ceased
-
2017
- 2017-09-19 WO PCT/EP2017/073537 patent/WO2018054855A1/en unknown
- 2017-09-19 JP JP2019536664A patent/JP6835974B2/en active Active
- 2017-09-19 CN CN201780058093.5A patent/CN109790838B/en not_active Expired - Fee Related
- 2017-09-19 BR BR112019005066A patent/BR112019005066A2/en not_active Application Discontinuation
- 2017-09-19 KR KR1020197010334A patent/KR102267530B1/en active IP Right Grant
- 2017-09-19 EP EP17780635.3A patent/EP3516227A1/en not_active Withdrawn
-
2019
- 2019-03-08 US US16/297,148 patent/US20190203712A1/en not_active Abandoned
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN114738279A (en) * | 2022-03-26 | 2022-07-12 | 上海坤彧节能科技有限公司 | Double-stage compression main machine with interstage cooling device |
Also Published As
Publication number | Publication date |
---|---|
CN109790838A (en) | 2019-05-21 |
EP3516227A1 (en) | 2019-07-31 |
JP2019529793A (en) | 2019-10-17 |
BR112019005066A2 (en) | 2019-06-18 |
KR102267530B1 (en) | 2021-06-18 |
JP6835974B2 (en) | 2021-02-24 |
DE102016011442A1 (en) | 2018-03-22 |
CN109790838B (en) | 2021-04-30 |
KR20190044685A (en) | 2019-04-30 |
WO2018054855A1 (en) | 2018-03-29 |
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