CN109964038A - Screw compressor system for commercial vehicle - Google Patents

Screw compressor system for commercial vehicle Download PDF

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Publication number
CN109964038A
CN109964038A CN201780070184.0A CN201780070184A CN109964038A CN 109964038 A CN109964038 A CN 109964038A CN 201780070184 A CN201780070184 A CN 201780070184A CN 109964038 A CN109964038 A CN 109964038A
Authority
CN
China
Prior art keywords
screw compressor
control unit
loop control
open loop
closed loop
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.)
Pending
Application number
CN201780070184.0A
Other languages
Chinese (zh)
Inventor
G·埃布拉尔
J-B·马勒斯考特
J·梅拉尔
T·魏因霍尔德
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of CN109964038A publication Critical patent/CN109964038A/en
Pending legal-status Critical Current

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Classifications

    • 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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/06—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of other than internal-axis type
    • 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
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • 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
    • 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
    • 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2207/00—External parameters
    • F04B2207/04—Settings
    • F04B2207/043—Settings of time
    • 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
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature
    • F04C2270/195—Controlled or regulated
    • 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
    • F04C2270/23—Working cycle timing control
    • 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
    • F04C2270/48—Conditions of a reservoir linked to a pump or machine
    • 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
    • F04C2270/60—Prime mover parameters
    • 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
    • F05B2270/00—Control
    • F05B2270/10—Purpose of the control system

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

The screw compressor system (100) that the present invention relates to a kind of for commercial vehicle, with at least one screw compressor (10), at least one screw compressor driver and at least one open loop and/or Closed Loop Control Unit (110), wherein, the open loop and/or Closed Loop Control Unit (110) are connect with the screw compressor driver, wherein, the open loop and/or Closed Loop Control Unit (110) are realized and are configured to, so that the open loop and/or Closed Loop Control Unit monitor the downtime of the screw compressor driver and the ratio of turn-on time in the operation of the screw compressor (10) and by the ratio open loop and/or closed-loop controls to preset range.

Description

Screw compressor system for commercial vehicle
Technical field
The present invention relates to a kind of screw compressor system for commercial vehicle, which has at least One screw compressor, the screw compressor have open loop and/or close-loop driven for the screw compressor At least one open loop of control and/or Closed Loop Control Unit.
Background technique
It is known from the state of the art the screw compressor for commercial vehicle.This screw compressor is for being, for example, commercialization The braking system of vehicle provides necessary compressed air.
In this regard, it is known that the compressor of oil is especially filled, especially it is also known that screw compressor, in these compressions There is the adjusting oil temperature of the task in machine.This usually realizes that the oil cooler and filling are oily by the oil cooler outside setting Compressor connected with oil return line via heat control valve.Oil cooler is that there are two the heat exchanges in circuit separated from each other for tool herein Device, wherein liquid, i.e. compressor oil of the first circuit setting for heat, and second servo loop is arranged for cooling down liquid.Such as it can Using use air, with antifreezing agent or other oil aqueous mixtures as cool down liquid.
Then, which must connect with compressor oil circuit via pipe fitting or hose and must assure that oil return line It does not leak.
In addition, the volume of the outside must be filled oil, to also increase oily total amount.Therefore system inertia is increased. In addition, oil cooler must mechanically be arranged and fix or by be located at surrounding holding meanss otherwise by separated guarantor Device is held to place and fix, this needs additional fixed mechanism, and is also required to structure space.
A kind of screw compressor for being integrated with oil cooler as known to US 4,780,061.
In addition, 37 17 493 A1 of DE discloses a kind of screw-compression machine equipment being arranged in compact shell, There is oil cooler on the electric notor of screw compressor.
Such screw compressor is for example via known to 10 2,004 060 417 B4 of DE.
Summary of the invention
The task of the present invention is, further construction starts the screw compressor system for referring to type in an advantageous manner, In particular so that the open loop and/or close-loop driven control of screw compressor simplifiedly and can be constructed reliably.
The task is solved according to the present invention by the screw compressor system of the feature with claim 1.Accordingly Regulation, a kind of screw compressor system for commercial vehicle are equipped at least one screw compressor, at least one screw Compressor drive and at least one open loop and/or Closed Loop Control Unit, wherein the open loop and/or Closed Loop Control Unit with The screw compressor driver connection, wherein the open loop and/or Closed Loop Control Unit are designed and are configured in this way, so that The open loop and/or Closed Loop Control Unit monitor the shut-down of screw compressor driver in the operation of the screw compressor The ratio of time and turn-on time and by the ratio opened loop control and/or closed-loop control to preset range.
The present invention is based on following basic conceptions: determining by the way that the ratio of downtime and turn-on time are also substantially common The temperature of screw compressor.It is sufficient that according to the structural shape of screw compressor, by by downtime and connection The ratio opened loop control of time can run screw compressor in very narrow temperature range of operation on preset range. The screw rod that is engaged with each other and being guided through the oil of screw compressor and compressed air causes heat to increase, thus logical Cross correspondingly select screw compressor driver downtime and turn-on time ratio also can simultaneously opened loop control and/ Or closed-loop control, the heat for setting screw compressor.
Such as it can be stated that the open loop and/or Closed Loop Control Unit are the screw compressor system (that is, screw rods Formula compressor or screw compressor driver) component part.Thus it constitutes compact structure and outside need not be used Component.
But in principle it is also recognized that the open loop and/or Closed Loop Control Unit are the groups of the air treatment system of commercial vehicle At part.Corresponding control unit is had existed herein, which can simply be used collectively.
It is also recognized that the open loop and/or Closed Loop Control Unit are the engine control section or vehicle control section of commercial vehicle Component part.It also can be realized the already existing component using commercial vehicle herein.
But in principle it is also recognized that the open loop and/or Closed Loop Control Unit are configured to individual open loop and/or closed loop control Unit processed.This for example can be realized simple assembly and simple replacement or simple upgrading.
Furthermore it can be stated that the range selects in this way, so that there are the ratio of following downtime and turn-on time, Wherein, turn-on time accounts for about 20 to 50%, especially greater than 30%.When being connected in this of downtime and turn-on time ratio Between between about 20 to 40%, especially greater than 30%, the ratio have proven to it is relatively advantageous, so as to make Running temperature keeps substantial constant.Furthermore following advantage is obtained, by the turn-on time for ensuring downtime and turn-on time Ratio greater than 30%, so that running temperature keeps sufficiently high, it is wet inside screw compressor also reliably to avoid Gas is formed or condensation.
Furthermore it can be stated that the open loop and/or Closed Loop Control Unit are designed and configured in this way so that the open loop and/or Closed Loop Control Unit influences the revolving speed of screw compressor driver in this way, so that the downtime of screw compressor driver It is maintained in the preset range with the ratio of turn-on time.Herein substantially from following content, in screw compressor The whole service time on should provide specific air supply and by defining or limiting or improve screw compressor The revolving speed of driver on total run time keep compressed air production in the case where can also influence screw compressor drive It moves the downtime of device and the ratio of turn-on time and therefore the ratio can be maintained in the preset range.
Especially it can be stated that the open loop and/or Closed Loop Control Unit are designed and configured in this way so that the open loop and/ Or Closed Loop Control Unit remains that the revolving speed of screw compressor driver is greater than minimum speed.Revolving speed is kept to be greater than minimum turn The possibility of speed is based on following basic conception: since certain minimum speed just limitation loss power and screw pressure Contracting machine driver needs less energy for generating the compressed air of specific quantity.In other words, thus, it is possible to generally improve screw rod The efficiency of formula compressor.Therefore for example it is known that function is lost when being lower than the minimum speed of about 1500 to 2500 rev/min Rate can rise strongly, to should avoid being lower than the minimum speed as far as possible.
Detailed description of the invention
Other details and advantage of the invention should be explained in more detail by the embodiment being shown in the accompanying drawings now.Its In:
Fig. 1 shows the schematic cross sectional views of screw compressor according to the invention；And
Fig. 2 shows the schematic diagrames of screw compressor system according to the invention.
Specific embodiment
Fig. 1 shows the schematic cross sectional views of the screw compressor 10 in the embodiment of the present invention meaning.
Screw compressor 10 has for screw compressor 10 to be mechanically fixed against the electricity not being shown specifically here Fixed flange 12 on motor.
However input shaft 14 is shown, the torque of electric notor is transferred to one of two screw rods 16,18, i.e. via the input shaft On screw rod 16.
Screw rod 18 engages with screw rod 16 and via the screw drive.
Screw compressor 10 has shell 20, and the main component of screw compressor 10 is arranged in the shell.
Shell 20 is filled oil 22.
In air input side, it is equipped on the shell 20 of screw compressor 10 and enters adapter tube 24.Herein into adapter tube 24 It constitutes in this way, so that being disposed with air filter 26 on it.In addition, radially entering on adapter tube 24 to enter equipped with air in air Mouth 28.
Bullet is equipped in entering adapter tube 24 and the region entered between the position where adapter tube 24 is arranged on the housing 20 The valve seat 30 of spring load, the valve seat are configured to axial seal herein.
The valve seat 30 is used as check-valves.
It is equipped with air delivery passage 32 in 30 downstream of valve seat, which gives air delivery to described two screw rods 16、18。
The air discharge duct part 34 with riser culverts 36 is equipped in the outlet side of described two screw rods 16,18.
It is equipped with temperature sensor 38 in the terminal area of riser culverts 36, oil temperature can be monitored by the temperature sensor.
In addition, being equipped with the holder 40 for air oil strain element 42 in air discharge domain.
Holder 40 for air oil strain element is in the assembled condition in the region (also as shown in Figure 1) towards bottom With air oil strain element 42.
In addition, it is equipped with corresponding strainer or known filtering and oil separating device 44 in the inside of air oil strain element 42, It is not specifically designated in detail.
In intermediate upper area, with reference to the state (that is, as shown in Figure 1) for assembling and being ready to operation, it to be used for air The holder 40 of oil strain element has air outlet opening 46, which passes to check-valves 48 and minimum pressure valve 50.Check-valves 48 and minimum pressure valve 50 also may be constructed in a common combined valve.
And then check-valves 48 is equipped with air outlet slit 51.
Air outlet slit 51 is usually connect with corresponding known compressed air customer.
In order to make oil 22 that is in air oil strain element 42 and separating in the air oil strain element flow back again Into shell 20, riser culverts 52 are equipped with, which exists in the output end of the holder 40 for air oil strain element 42 Being transitioned at shell 20 has strainer valve and check-valves 54.
In 54 downstream of strainer valve and check-valves, nozzle 56 is equipped in housing bore.Oil return line 58 back passes to screw rod 16 Or the substantially intermediate region of screw rod 18, to make oil 22 be back to the screw rod again.
Purge cock 59 is equipped in the bottom section under assembled state in shell 20.It can via the purge cock 59 It is drained the oil opening accordingly with opening, oily 22 openings that can drain the oil via this are released.
There is also attachment 60 in the lower zone of shell 20, oil strainer 62 is fixed in the attachment.Oil 22 is first First enter channel 64 via the oil strainer of arrangement within the casing 20 and is directed to heat control valve 66.
Replace heat control valve 66 that can also be equipped with open loop and/or closed-loop control device, is filled by the open loop and/or closed-loop control It sets the oil temperature that can monitor the oil 22 in shell 20 and the oil temperature can be adjusted to desired value.
Then, in the oil-in that 66 downstream of heat control valve is oil strainer 62, which leads back pipeline 68 via intermediate It leads back oil 22 again to screw rod 18 or screw rod 16, but also leads back to the bearing 70 by oil lubrication of axis 14.In the area of bearing 70 Nozzle 72 also is provided in domain, the nozzle within the casing 20 with lead back pipeline 68 and be arranged in association.
Cooler 74 is connected in attachment 60.
(referring to assembled state) in the upper area of shell 20, there are safety valves 76, can reduce via the safety valve Excessive pressure in shell 20.
In 50 upstream of minimum pressure valve there are bypass line 78, which passes to pressure reducing valve 80.Via by with sky Pressure reducing valve 80 for connecting to be steered of gas delivery section 32, air can back into the region of air intake 28.In the area It can be equipped with the exhaust valve not being shown specifically in domain and or be equipped with nozzle (reduced diameter portion of transfer pipeline point).
In addition, fuel level sensor 82 can be equipped in the outer wall of shell 20 substantially in the height of pipeline 34.The oil level Sensor 82 for example can be optical sensor and be achieved and install, and make it possible to identify by sensor signal Oil level is on fuel level sensor 82 in operation or fuel level sensor 82 is exposed and thus oil level accordingly decreases.
It can also be equipped with alarm unit in association with the monitoring, which disappears corresponding failure message or warning Breath output or the user for passing to system.
The function of screw compressor 10 shown in FIG. 1 is as follows herein:
Air via air intake 28 convey and via check-valves 30 reach screw rod 16,18, air the screw rod that In compressed.Compressed gas mixture is directly blown on temperature sensor 38, and the gas mixture is between 5 to 16 times Coefficient after screw rod 16 and 18 by compressively pass through discharge line 34 via rise pipe fitting 36 risen.
Still part have oil particles air then be directed into air oil strain element 42 via holder 40 and It is entered as long as having reached corresponding minimum pressure in air discharge duct road 51.
Oil 22 in shell 20 is maintained at operation temperature via oil strainer 62 and when necessary via heat exchanger 74 Degree.
If you do not need to it is cooling, then it does not use and does not access heat exchanger 74 yet.
Corresponding access is realized via heat control valve 68.After purifying in oil strainer 64, oil is conveyed via pipeline 68 To screw rod 18 or screw rod 16, but also it is delivered to bearing 72.Oil 22 is supplied via pipeline 52,58 is led back in screw rod 16 or screw rod 18, It is realized in air oil strain element 42 in the purification of this oil 22.
Drive the screw rod 16 and 18 of screw compressor 10 via the electric notor not being shown specifically, the electric notor is by its turn The screw rod 16 that square is transmitted to via axis 14 and engages with axis 18.
Ensure for example exist in the outlet side of screw rod 16,18 under operation via the pressure reducing valve 80 not being shown specifically High pressure will not be stranded lock in the region of transfer pipeline 32, and especially in compressor start in the area of transfer pipeline 32 Always there is low input pressure, especially atmospheric pressure in domain.Otherwise, as the starting of compressor will be first in screw rod 16 and 18 Outlet side there are very high pressure, which will be so that drive motor be overloaded.
Fig. 2 with illustrate to illustrate it is according to the invention with screw compressor 10 shown in FIG. 1 and have open loop and The screw compressor system 100 of Closed Loop Control Unit 110.
Open loop and Closed Loop Control Unit 110 are configured to the component part of screw compressor system 100 herein.
But in principle also it can be stated that open loop and Closed Loop Control Unit 110 are configured to the air treatment system of commercial vehicle Component part, the engine control section of commercial vehicle or vehicle control section component part or be configured to individual open loop and closed loop control Unit 110 processed.
Open loop and the design and configuration in this way of Closed Loop Control Unit 110, so that the open loop and/or Closed Loop Control Unit are described In the operation of screw compressor 10 monitor for drive screw rod 16 and 18 screw compressor driver downtime and The ratio of turn-on time and by the ratio opened loop control or closed-loop control on preset range.
Here, the range selects in this way, so that there are the ratios of following downtime and turn-on time, wherein connect Time is greater than 30%.Range of the turn-on time between 30% to 50% is especially selected herein, thus therefore downtime exists Between 50% to 70% and turn-on time is about between 30% to 50%.
Therefore, when turn-on time being about 30%, downtime accounts for about 70%.
In order to also the ratio of downtime and turn-on time be made correspondingly to keep constant, open loop and Closed Loop Control Unit 110 furthermore designs and configuration in this way, so that its revolving speed for influencing screw compressor driver together.
It should be noted here that by the revolving speed for reducing or improving screw compressor driver, in the whole service duration It is upper to provide desired air supply by screw compressor 10, but tieed up in the ratio of this downtime and turn-on time It holds.
In order to economically and high energy efficiency work, furthermore remained turn by open loop and Closed Loop Control Unit 110 herein Speed is greater than minimum speed.
This based on the realisation that, be lower than minimum speed when, the specific energy absorption of screw compressor driver is (that is, example Energy as needed the air for compressing one cubic metre (m3)) very strongly rise.In other words, it therefore avoids generating excessively high Loss power or excessively high loss.
By keeping constant the ratio of downtime and turn-on time, therefore generally realize that screw compressor 10 exists It is able to maintain in terms of running temperature on the whole service duration relative constant.
By keeping compressor in terms of running temperature on the whole service duration, reliably avoid in screw pressure It can be condensed in the shell 20 of contracting machine 10.
It is maintained at running temperature by constant running temperature and screw compressor 10, is reliably avoided in shell 20 In condensation.
Reference signs list
10 screw compressors
12 fixed flanges
14 input shafts
16 screw rods
18 screw rods
20 shells
22 oil
24 enter adapter tube
26 air filters
28 air intakes
30 valve seats
32 air delivery passages
34 air discharge duct parts
36 riser culverts
38 temperature sensors
40 are used for the holder of air oil strain element
42 air oil strain elements
44 strainers or known filtering and oil separating device
46 air outlet openings
48 check-valves
50 minimum pressure valves
51 air outlet slits
52 riser culverts
54 strainer valves and check-valves
56 nozzles
58 oil return lines
59 purge cocks
60 attachments
60a outer ring
60b inner ring
62 oil strainers
64 oil strainers enter channel
66 heat control valves
68 lead back pipeline
70 bearings
72 nozzles
76 safety valves
78 bypass lines
80 relief valves
82 fuel level sensors
100 screw compressor systems
110 opened loop controls and Closed Loop Control Unit

Claims (8)

1. a kind of screw compressor system (100) for commercial vehicle, at least one screw compressor (10), at least One screw compressor driver 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 connect with the screw compressor driver, wherein the open loop and/or Closed Loop Control Unit (110) it is designed and configured to, so that the open loop and/or Closed Loop Control Unit are supervised in the operation of the screw compressor (10) It controls the downtime of the screw compressor driver and the ratio of turn-on time and by the ratio opened loop control and/or closes Ring is controlled to preset range.
2. screw compressor system (100) according to claim 1, which is characterized in that the open loop and/or closed loop control Unit (110) processed is the component part of the screw compressor system (10).
3. screw compressor system (100) according to claim 1, which is characterized in that the open loop and/or closed loop control Unit (110) processed is the component part of the air treatment system of commercial vehicle.
4. screw compressor system (100) according to claim 1, which is characterized in that the open loop and/or closed loop control Unit (110) processed is the engine control section of commercial vehicle or the component part of vehicle control section.
5. screw compressor system (100) according to claim 1, which is characterized in that the open loop and/or closed loop control Unit (110) processed is individual open loop and/or Closed Loop Control Unit (110).
6. screw compressor system (100) according to any one of the preceding claims, which is characterized in that the range In this way select so that there are the ratios of following downtime and turn-on time, wherein turn-on time account for about 20% to 40%, it is especially greater than 30%.
7. screw compressor system (100) according to any one of the preceding claims, which is characterized in that the open loop And/or Closed Loop Control Unit (110) is designed and configured to, so that the open loop and/or Closed Loop Control Unit influence the screw The revolving speed of compressor drive, so that the downtime of the screw compressor driver and the ratio of turn-on time are maintained at In the preset range.
8. screw compressor system (100) according to claim 7, which is characterized in that the open loop and/or closed loop control Unit (110) processed is designed and configured to, so that the open loop and/or Closed Loop Control Unit remain the screw compressor The revolving speed of driver is greater than minimum speed.
CN201780070184.0A 2016-09-21 2017-09-19 Screw compressor system for commercial vehicle Pending CN109964038A (en)

Applications Claiming Priority (3)

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DE102016011507.6A DE102016011507A1 (en) 2016-09-21 2016-09-21 Screw compressor system for a commercial vehicle
DE102016011507.6 2016-09-21
PCT/EP2017/073579 WO2018054878A1 (en) 2016-09-21 2017-09-19 Screw compressor system for a utility vehicle

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CN109964038A true CN109964038A (en) 2019-07-02

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EP (1) EP3516230A1 (en)
JP (1) JP2019536942A (en)
KR (1) KR20190045946A (en)
CN (1) CN109964038A (en)
BR (1) BR112019005057A2 (en)
DE (1) DE102016011507A1 (en)
WO (1) WO2018054878A1 (en)

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KR20190045946A (en) 2019-05-03
BR112019005057A2 (en) 2019-06-18
WO2018054878A1 (en) 2018-03-29
EP3516230A1 (en) 2019-07-31
US20190338778A1 (en) 2019-11-07
JP2019536942A (en) 2019-12-19

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