CN109964037B - Screw compressor system for a commercial vehicle - Google Patents
Screw compressor system for a commercial vehicle Download PDFInfo
- Publication number
- CN109964037B CN109964037B CN201780070183.6A CN201780070183A CN109964037B CN 109964037 B CN109964037 B CN 109964037B CN 201780070183 A CN201780070183 A CN 201780070183A CN 109964037 B CN109964037 B CN 109964037B
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- Prior art keywords
- screw compressor
- loop
- closed
- control unit
- open
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/28—Safety arrangements; Monitoring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/05—Speed
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/19—Temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2105—Oil temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The invention relates to a screw compressor system (100) for a utility vehicle, having at least one screw compressor (10), at least one screw compressor drive, at least one temperature sensor (38) and at least one open-loop and/or closed-loop control unit (110), wherein the open-loop and/or closed-loop control unit (110) is connected to the screw compressor drive and to the temperature sensor (38), wherein the open-loop and/or closed-loop control unit (110) is designed and configured in such a way that it actuates the screw compressor drive with respect to the rotational speed of the screw compressor drive as a function of a temperature threshold signal obtained from the temperature sensor (38).
Description
Technical Field
The invention relates to a screw compressor system for a commercial vehicle, having at least one screw compressor with at least one open-loop and/or closed-loop control unit for the open-loop and/or closed-loop drive control of the screw compressor.
Background
Screw compressors for commercial vehicles are known from the prior art. Such screw compressors are used, for example, to supply the necessary compressed air for the brake system of a commercial vehicle.
In this connection, compressors, in particular filled with oil, in particular also screw compressors, are known, in which the task of regulating the oil temperature is present. This is usually achieved by means of an externally arranged oil cooler which is connected to the oil-filled compressor and the oil circuit via a thermostatic valve. The oil cooler is a heat exchanger having two circuits separated from each other, wherein a first circuit is provided for a hot fluid, i.e. compressor oil, and a second circuit is provided for cooling the liquid. For example, air, a water mixture with antifreeze or other oils can be used as cooling liquid.
The oil cooler must then be connected to the compressor oil circuit via a pipe or hose and it must be ensured that the oil circuit does not leak.
Furthermore, the outer volume must be filled with oil, thereby also increasing the total amount of oil. Thus increasing the system inertia. Furthermore, the oil cooler must be arranged and fixed mechanically, either by means of a holding device located around it or by means of a separate holding device, which requires additional fixing means and also requires installation space.
From US 4,780,061 a screw compressor with an integrated oil cooling device is known.
Furthermore, DE 3717493 a1 discloses a screw compressor arrangement arranged in a compact housing, which has an oil cooler on the electric motor of the screw compressor.
A screw compressor of this type is known, for example, from DE 102004060417B 4.
Disclosure of Invention
The object of the present invention is to further develop a screw compressor system of the type mentioned at the outset in an advantageous manner, in particular such that an open-loop and/or closed-loop drive control of the screw compressor can be configured in a simplified and reliable manner.
This object is achieved according to the invention by a screw compressor system for a utility vehicle having the features of the invention. In accordance with this specification, a screw compressor system for a utility vehicle has at least one screw compressor, at least one screw compressor drive, at least one temperature sensor and at least one open-loop and/or closed-loop control unit, wherein the open-loop and/or closed-loop control unit is connected to the screw compressor drive and to the temperature sensor, wherein the open-loop and/or closed-loop control unit is designed and configured in such a way that it actuates the screw compressor drive as a function of a temperature threshold signal obtained from the temperature sensor with regard to the rotational speed of the screw compressor drive.
The invention is based on the following basic idea: temperature management of the screw compressor system can be achieved by operating the screw compressor drive accordingly as a function of the temperature in the screw compressor. The temperature of the screw compressor is also decisively influenced by the rotational speed of the screw compressor drive. If a certain temperature is reached, the temperature can be increased or decreased accordingly by adapting the rotational speed of the screw compressor drive. In particular, the screw compressor system may be relatively large, so that a certain inertia may be generated which causes a temperature change based on the amount of oil present in the screw compressor. It is also conceivable to relate to a screw compressor system which is usually designed for part-load operation or low-load operation and does not have to be operated continuously in full-load operation.
For example, it can be provided that the open-loop and/or closed-loop control unit is a component of the screw compressor system. This results in a compact construction and eliminates the need for external components.
In principle, however, it is also conceivable for the open-loop and/or closed-loop control unit to be a component of an air treatment system of a commercial vehicle. In this case, corresponding controls are already available, which can be used together in a simple manner.
It is also conceivable for the open-loop and/or closed-loop control unit to be a component of an engine control unit or a vehicle control unit of a commercial vehicle. It is also possible to use already existing components of the utility vehicle.
In principle, however, it is also conceivable for the open-loop and/or closed-loop control unit to be designed as a separate open-loop and/or closed-loop control unit. This enables, for example, simple assembly and simple replacement or simple upgrading.
Furthermore, it can be provided that the open-loop and/or closed-loop control unit is designed and configured in such a way that it switches off the screw compressor drive when a temperature threshold signal is obtained which indicates that a predetermined temperature threshold is exceeded in the screw compressor. The temperature reduction in the screw compressor can thus be achieved simply and effectively in a very short time. Without operating the screw compressor by switching off the screw compressor drive, no further heat increase is caused in the screw compressor, so that the screw compressor can be cooled.
It is furthermore conceivable that the open-loop and/or closed-loop control unit is embodied and configured such that it is only capable of effecting switching on of the screw compressor drive when it obtains a temperature threshold signal which indicates that a temperature in the screw compressor is below a predetermined temperature threshold. In principle, the temperature threshold signal indicative of a temperature below a predetermined temperature threshold in the screw compressor is different from the temperature threshold signal obtained by the open-loop and/or closed-loop control unit by which the screw compressor drive is triggered to shut down. But these temperature threshold signals may also be identical. By preventing the screw compressor from starting or restarting when the temperature is too high, a simple but at the same time reliable open-loop or closed-loop control of the temperature in the screw compressor system or in the screw compressor can likewise be achieved.
It can be provided that the screw compressor system does not have a thermostatic valve. In principle, it is also conceivable that the temperature management of the screw compressor can be operated effectively on the basis of the design of the open-loop and/or closed-loop control unit in such a way that no heat-related connection is required at all to the oil cooling circuit, which usually has a thermostatic valve. This component of the screw compressor system can thus be omitted.
In principle, it can also be provided that the screw compressor system does not have a heat exchanger for oil cooling. By eliminating this relatively expensive component, the structure of the screw compressor system as a whole can be simplified.
Drawings
Further details and advantages of the invention shall now be explained in more detail by means of embodiments shown in the drawings. Wherein:
FIG. 1 shows a schematic cross-sectional view of a screw compressor according to the present invention; and
FIG. 2 shows a schematic view of a screw compressor system according to the present invention.
Detailed Description
Fig. 1 shows a schematic cross-sectional view of a screw compressor 10 in the sense of an embodiment of the invention.
However, an input shaft 14 is shown, via which the torque of the electric motor is transmitted to one of the two screws 16, 18, i.e. the screw 16.
The screw 18 is engaged with the screw 16 and is driven via the screw.
The housing 20 is filled with oil 22.
On the air inlet side, an inlet connection 24 is provided on the housing 20 of the screw compressor 10. The intake connector 24 is designed such that an air filter 26 is arranged thereon. Furthermore, an air inlet 28 is provided radially on the air inlet connector 24.
In the region between the inlet socket 24 and the point at which the inlet socket 24 is arranged on the housing 20, a spring-loaded valve seat 30 is provided, which is designed here as an axial seal.
The valve seat 30 functions as a check valve.
Downstream of the valve seat 30, an air supply duct 32 is provided, which supplies air to the two screws 16, 18.
On the output side of the two screws 16, 18, an air outlet pipe 34 with a rising line 36 is provided.
In the end region of the rising line 36, a temperature sensor 38 is provided, by means of which the oil temperature can be monitored.
Furthermore, a holder 40 for an air filter element 42 is provided in the air outlet region.
The holder 40 for the air filter element has an air filter element 42 in the region facing the bottom in the assembled state (also shown in fig. 1).
Furthermore, a corresponding filter screen or a known filter and oil separator device 44, which is not described in detail in more detail, is provided in the interior of the air filter element 42.
In the upper central region, with reference to the assembled and ready-to-operate state (i.e. as shown in fig. 1), the holder 40 for the air filter element has an air outlet opening 46 which opens into a check valve 48 and a minimum pressure valve 50. The check valve 48 and the minimum pressure valve 50 can also be formed in a common combined valve.
An air outlet 51 is provided next to the check valve 48.
The air outlet 51 is usually connected to a corresponding known compressed air consumer.
In order to return the oil 22 which is located in the air filter element 42 and is separated in it into the housing 20 again, a rising line 52 is provided which has a filter valve and a check valve 54 at the transition to the housing 20 at the outlet of the holder 40 for the air filter element 42.
Downstream of the filter and check valves 54, a nozzle 56 is provided in the housing bore. The return line 58 leads back to approximately the middle region of the screw 16 or the screw 18, in order to return the oil 22 to the screw again.
In the bottom region of the housing 20 in the assembled state, an oil drain plug 59 is provided. Via the drain plug 59, the respective drain opening can be opened, via which the oil 22 can be drained.
There is also an attachment 60 in the lower region of the housing 20, on which an oil filter 62 is fixed. The oil 22 is first led to a thermostatic valve 66 via an oil filter inlet channel 64 arranged in the housing 20.
Instead of the thermostat valve 66, an open-loop and/or closed-loop control device can also be provided, by means of which the oil temperature of the oil 22 located in the housing 20 can be monitored and set to a desired value.
Downstream of the thermostatic valve 66 is then an oil inlet of the oil filter 62, which leads the oil 22 back again to the screw 18 or the screw 16 via an intermediate return line 68, but also to an oil-lubricated bearing 70 of the shaft 14. In the region of the bearing 70, a nozzle 72 is also provided, which is arranged in the housing 20 in conjunction with the return line 68.
The cooler 74 is connected to the attachment portion 60, as will be explained in more detail below with reference to fig. 1.
In the upper region of the housing 20 (with reference to the assembled state) there is a safety valve 76, via which an excessive pressure in the housing 20 can be reduced.
Upstream of the minimum pressure valve 50 there is a bypass line 78 which leads to a pressure relief valve 80. Via this pressure reducing valve 80, which is actuated by means of the connection to the air supply 32, air can be returned into the region of the air inlet 28. In this region, an exhaust valve, not shown in detail, and also a nozzle (reduced diameter section of the supply line) can be provided.
Furthermore, a fuel level sensor 82 may be provided in the outer wall of the housing 20, approximately at the level of the line 34. The fuel level sensor 82 can be, for example, an optical sensor and is embodied and arranged in such a way that it can be detected by means of a sensor signal whether the fuel level is above the fuel level sensor 82 during operation or the fuel level sensor 82 is exposed and the fuel level is accordingly lowered.
In connection with this monitoring, an alarm unit can also be provided, which outputs or transmits corresponding fault messages or warning messages to a user of the system.
The function of the screw compressor 10 shown in fig. 1 is the following:
air is fed in via an air inlet 28 and reaches the screws 16, 18 via check valves 30, where it is compressed. The compressed mixture of oil and gas, which rises after the screws 16 and 18 in compression by a factor of between 5 and 16 via the riser 36 through the discharge line 34, is blown directly onto the temperature sensor 38.
The air still partially containing oil particles is then conducted via the holder 40 into the air filter element 42 and, as soon as the corresponding minimum pressure is reached, into the air outlet line 51.
The oil 22 located in the housing 20 is maintained at operating temperature via the oil filter 62 and, if necessary, via the heat exchanger 74.
If cooling is not required, the heat exchanger 74 is not used and is not switched in.
The corresponding access is effected via the thermostatic valve 68. After purification in the oil filter 64, the oil is conveyed via a line 68 to the screw 18 or the screw 16, but also to a bearing 72. The screw 16 or the screw 18 is supplied with oil 22 via the return lines 52, 58, wherein the cleaning of the oil 22 takes place in the air filter element 42.
The screws 16 and 18 of the screw compressor 10 are driven via an electric motor, not shown in detail, which transmits its torque via the shaft 14 to the screw 16, which in turn meshes with the shaft 18.
A pressure relief valve 80, which is not shown in detail, ensures that the high pressure prevailing in the operating state, for example on the outlet side of the screws 16, 18, does not become trapped in the region of the feed line 32, but that a low inlet pressure, in particular atmospheric pressure, is always present in the region of the feed line 32, in particular when the compressor is started. Otherwise, with the start of the compressor, there will be a very high pressure on the output side of the screws 16 and 18 in the first place, which would overload the drive motor.
FIG. 2 schematically illustrates a screw compressor system 100 having the screw compressor 10 shown in FIG. 1 in accordance with the present invention.
The screw compressor system 100 furthermore has an open-loop and/or closed-loop control unit 110 which is connected to the temperature sensor 38 and to the drives of the screws 16 and 18 of the screw compressor (electric motors not shown in detail which transmit their torque to the input shaft 14).
The open-loop and closed-loop control unit 110 is here formed as an integral part of the screw compressor 10.
In principle, however, it is also possible to design the open-loop and closed-loop control unit 110 as a component of an air treatment system, not shown in detail, of a commercial vehicle, as a component of an engine control or a vehicle control of the commercial vehicle, or as a separate open-loop and closed-loop control unit 110.
The open-loop and/or closed-loop control unit 110 is implemented and configured such that it operates the screw compressor drive in terms of its rotational speed in accordance with a temperature threshold signal obtained from the temperature sensor 38.
In particular, it is provided here that the open-loop and closed-loop control unit 110 switches off the screw compressor drive when a temperature threshold signal is obtained which indicates that a predetermined temperature threshold is exceeded in the screw compressor 10.
Restarting the screw compressor can only be accomplished when a temperature threshold signal from the temperature sensor 38 indicating a temperature below a predetermined temperature threshold in the screw compressor 10 is transmitted to the open and closed loop control unit 110.
The temperature threshold for switching the screw compressor 10 on and off is preferably selected in the same way in order to be able to carry out a simple implementation.
In principle, however, it can also be provided that different threshold values are provided for this purpose.
The temperature threshold may be selected, for example, at about 10% to 30% above the normal operating temperature.
This can be achieved by the configuration shown in fig. 2, without the screw compressor system 100 or the screw compressor 10 having to have a thermostatic valve 66 and also no heat exchanger 74.
List of reference numerals
10 screw compressor
12 fixing flange
14 input shaft
16 screw
18 screw
20 casing
22 oil
24 entry nipple
26 air filter
28 air inlet
30 valve seat
32 air delivery channel
34 air outlet pipe
36 ascending pipeline
38 temperature sensor
40 holder for an air filter element
42 air filter element
44 screens or known filtering and oil separating devices
46 air outlet opening
48 check valve
50 minimum pressure valve
51 air outlet
52 rising line
54 filter valve and check valve
56 spray nozzle
58 return line
59 oil drain plug screw
60 attachment part
60a outer ring
60b inner ring
62 oil filter
64 oil filter inlet passage
66 thermostatic valve
68 lead-back pipeline
70 bearing
72 nozzle
74 cooler, heat exchanger
76 safety valve
78 bypass line
80 pressure relief valve
82 oil level sensor
100 screw compressor system
110 open-loop and/or closed-loop control unit
Claims (5)
1. Screw compressor system (100) for a commercial vehicle, having at least one screw compressor (10), at least one screw compressor drive, at least one temperature sensor (38) by means of which an oil temperature can be monitored, and at least one open-loop or closed-loop control unit (110), wherein the open-loop or closed-loop control unit (110) is connected to the screw compressor drive and to the temperature sensor (38), wherein the open-loop or closed-loop control unit (110) is designed and configured such that it actuates the screw compressor drive with respect to its rotational speed as a function of a temperature threshold signal obtained from the temperature sensor (38), wherein the rotational speed of the screw compressor drive influences the temperature of the screw compressor and the screw compressor system (100) has no heat exchanger (74) for oil cooling, wherein the open-loop or closed-loop control unit (110) is designed as a separate open-loop or closed-loop control unit (110) independent of the screw compressor (10), wherein an air outlet pipe (34) having a rising line (36) is provided on the output side of the screws (16, 18) of the screw compressor, and wherein the temperature sensor (38) is provided in the region of a terminal end of the rising line (36), wherein the open-loop or closed-loop control unit (110) is designed and configured in such a way that it switches off the screw compressor drive when a temperature threshold signal is obtained which indicates that a predetermined temperature threshold is exceeded in the screw compressor (10).
2. The screw compressor system (100) of claim 1, wherein the open-loop or closed-loop control unit (110) is a component of an air handling system of a commercial vehicle.
3. The screw compressor system (100) of claim 1, wherein the open-loop or closed-loop control unit (110) is an integral part of an engine control or a vehicle control of a commercial vehicle.
4. The screw compressor system (100) of any one of claims 1 to 3, wherein the open-loop or closed-loop control unit (110) is implemented and configured such that it is only capable of enabling switching on of a screw compressor drive when it obtains a temperature threshold signal indicative of a temperature below a predetermined temperature threshold in the screw compressor (10).
5. The screw compressor system (100) of any one of claims 1 to 3, wherein the screw compressor system (100) is free of a thermostatic valve (66).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016011508.4 | 2016-09-21 | ||
| DE102016011508.4A DE102016011508A1 (en) | 2016-09-21 | 2016-09-21 | Screw compressor system for a commercial vehicle |
| PCT/EP2017/073581 WO2018054879A1 (en) | 2016-09-21 | 2017-09-19 | Screw compressor system for a utility vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109964037A CN109964037A (en) | 2019-07-02 |
| CN109964037B true CN109964037B (en) | 2022-03-29 |
Family
ID=59982348
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780070183.6A Expired - Fee Related CN109964037B (en) | 2016-09-21 | 2017-09-19 | Screw compressor system for a commercial vehicle |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US20190376517A1 (en) |
| EP (1) | EP3516225A1 (en) |
| JP (1) | JP6896083B2 (en) |
| KR (1) | KR20190047725A (en) |
| CN (1) | CN109964037B (en) |
| BR (1) | BR112019005118A2 (en) |
| DE (1) | DE102016011508A1 (en) |
| WO (1) | WO2018054879A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114183952B (en) * | 2021-12-21 | 2023-09-15 | 宁波奥克斯电气股份有限公司 | Refrigerant recovery control method and refrigerant recovery unit |
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| DE3422396A1 (en) * | 1984-06-15 | 1985-12-19 | Brückner-Apparatebau GmbH, 6120 Erbach | Process and apparatus for the wet treatment of textile material |
| DE3422398A1 (en) * | 1984-06-15 | 1985-12-19 | Knorr-Bremse GmbH, 8000 München | Method and apparatus for operating a screw compressor installation |
| 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 |
| US5653585A (en) * | 1993-01-11 | 1997-08-05 | Fresco; Anthony N. | Apparatus and methods for cooling and sealing rotary helical screw compressors |
| JP2003003981A (en) * | 2001-06-21 | 2003-01-08 | Kobe Steel Ltd | Method of operating screw compressor |
| DE102004060417B4 (en) | 2004-12-14 | 2006-10-26 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compact screw compressor for mobile use in a vehicle |
| DE102005010690B4 (en) * | 2005-03-09 | 2007-04-12 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Oil-injected compressor with temperature switch |
| US8561921B1 (en) * | 2009-10-16 | 2013-10-22 | Steve C. Showman | Plural component mixing system |
| GB201122142D0 (en) * | 2011-12-21 | 2012-02-01 | Venus Systems Ltd | Centrifugal compressors |
| DE102012002654A1 (en) * | 2012-02-10 | 2013-08-14 | Liebherr-Hausgeräte Ochsenhausen GmbH | Refrigerator and/or freezer e.g. chest freezer, has regulating unit that switches ON and/or OFF of compressor for temperature control within refrigerated compartment in response to correlated parameters of temperature in compartment |
| CN202690458U (en) * | 2012-07-20 | 2013-01-23 | 上海优耐特斯压缩机有限公司 | Oil injection screw type air-cooled compressor |
| DE102013114374B4 (en) * | 2013-01-09 | 2019-10-31 | Secop Gmbh | Method for controlling the speed of a variable speed compressor |
| WO2015051019A1 (en) * | 2013-10-01 | 2015-04-09 | Trane International, Inc. | Rotary compressors with variable speed and volume control |
| JP2015078607A (en) * | 2013-10-15 | 2015-04-23 | 株式会社神戸製鋼所 | Starting device and starting method of compressor |
| DE102015001803A1 (en) * | 2015-02-12 | 2016-08-18 | Man Truck & Bus Ag | Method and device for assisting a driver of a vehicle, in particular a utility vehicle |
-
2016
- 2016-09-21 DE DE102016011508.4A patent/DE102016011508A1/en not_active Withdrawn
-
2017
- 2017-09-19 EP EP17777198.7A patent/EP3516225A1/en not_active Withdrawn
- 2017-09-19 WO PCT/EP2017/073581 patent/WO2018054879A1/en unknown
- 2017-09-19 JP JP2019536680A patent/JP6896083B2/en active Active
- 2017-09-19 KR KR1020197011047A patent/KR20190047725A/en not_active Application Discontinuation
- 2017-09-19 CN CN201780070183.6A patent/CN109964037B/en not_active Expired - Fee Related
- 2017-09-19 US US16/333,495 patent/US20190376517A1/en not_active Abandoned
- 2017-09-19 BR BR112019005118A patent/BR112019005118A2/en not_active IP Right Cessation
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| WO2018054879A1 (en) | 2018-03-29 |
| US20190376517A1 (en) | 2019-12-12 |
| JP6896083B2 (en) | 2021-06-30 |
| BR112019005118A2 (en) | 2019-06-04 |
| KR20190047725A (en) | 2019-05-08 |
| EP3516225A1 (en) | 2019-07-31 |
| JP2019536943A (en) | 2019-12-19 |
| CN109964037A (en) | 2019-07-02 |
| DE102016011508A1 (en) | 2018-03-22 |
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