US20060218959A1 - Refrigerant compressor - Google Patents
Refrigerant compressor Download PDFInfo
- Publication number
- US20060218959A1 US20060218959A1 US11/393,215 US39321506A US2006218959A1 US 20060218959 A1 US20060218959 A1 US 20060218959A1 US 39321506 A US39321506 A US 39321506A US 2006218959 A1 US2006218959 A1 US 2006218959A1
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- Prior art keywords
- switching
- refrigerant compressor
- valve
- compressor according
- cylinder
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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
- 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
- F04B49/22—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 means of valves
- F04B49/225—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 means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/067—Control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/24—Control not provided for in a single group of groups F04B27/02 - F04B27/22
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/06—Valve parameters
- F04B2201/0601—Opening times
- F04B2201/06011—Opening times of the inlet valve only
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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
- F25B2600/25—Control of valves
- F25B2600/2515—Flow valves
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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
- F25B2600/25—Control of valves
- F25B2600/2521—On-off valves controlled by pulse signals
Definitions
- the invention relates to a refrigerant compressor for refrigerating systems comprising at least one cylinder unit, which has a cylinder housing and a piston which can move in an oscillating manner in the cylinder housing, a cylinder head, with an inlet chamber, flowed through by an inlet flow of the at least one cylinder unit, and with an outlet chamber, passed through by an outlet flow of the at least one cylinder unit, and also a switching valve for interrupting the inlet flow.
- Refrigerant compressors of this type are known from the prior art; with these, the switching valve provides the possibility of permanently switching off or permanently switching on one or more cylinder units.
- This object is achieved in the case of a refrigerant compressor of the type described at the beginning by providing a control for activating the switching valve which, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than a shortest time period after which a temperature of an evaporator in the operating refrigerating system has risen by approximately 10% during an interruption of the inlet flow.
- the advantage of the solution according to the invention can be seen in that it opens up the possibility of operating in particular a reciprocating piston compressor in a lower part-load range with any desired part load, since the mass flow to be compressed can be set steplessly and as desired by the ratio of the opening intervals and the closing intervals within each switching interval.
- time periods that are adequately short are chosen for the switching intervals, so that, on account of the inertia of the reaction of the refrigerating system according to the invention to the switching intervals, only insubstantial temperature fluctuations that do not impair precise regulation of the temperature occur in the evaporator of the refrigerating systems.
- a further exemplary embodiment of a refrigerant compressor of the type described at the beginning provides a control for activating the switching valve which, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than approximately 10 seconds.
- Limiting the duration of the switching intervals in such a manner likewise creates the possibility in a way according to the invention of operating the refrigerant compressor in a lower part-load range with a part load that can be set as desired, without pressure fluctuations which impair the quality of the regulation of the refrigerating system occurring in said system.
- the switching intervals are longer than approximately 0.02 seconds.
- the switching intervals are longer than 0.05 seconds and particularly advantageous if the switching intervals are longer than 0.1 seconds.
- the switching valve It is particularly advantageous for switching the switching valve if the switching intervals correspond to a switching frequency which is less than an inherent or natural frequency of the switching valve.
- the switching intervals correspond to a switching frequency which is less than an inherent or natural frequency of the switching valve by a factor of 5.
- a particularly suitable solution provides that, in the lower part-load range, the control operates all the cylinder units of the refrigerant compressor in the switching intervals.
- time duration of the switching intervals a wide variety of solution possibilities are conceivable.
- a variant that is particularly advantageous for reasons of simplicity provides that the control operates with switching intervals that are of a constant time.
- Another advantageous solution provides that the control varies the switching intervals on the basis of a rotational drive speed of the refrigerant compressor.
- the switching valve is a servo valve.
- the servo valve comprises a valve body which can be actuated by a pressure associated with the pressure in the outlet chamber.
- valve body In order to ensure that the valve body does not automatically assume the end position brought about by the pressure in the outlet chamber, it is preferably provided that the valve body is acted upon by an elastic force accumulator acting counter to the effect of the pressure on the valve body.
- valve body is coupled to a switching piston which can be acted upon by a pressure associated with the pressure in the outlet chamber and is guided in a switching cylinder housing, and which then actuates the valve body.
- the switching piston and the switching cylinder housing enclose a switching cylinder chamber and if the pressure in the switching cylinder chamber is controllable.
- valve body and the switching piston form a unit which is guided in the switching cylinder housing.
- a servo valve of this type comprises a control valve which can be activated by the control.
- a control valve of this type is formed for example as a rapidly responding, electrically activatable solenoid valve or similarly constructed valve.
- control valve opens or closes a connecting channel between the control cylinder chamber and the outlet chamber, so that, in a simple manner, there is the possibility of acting upon the switching piston with medium under the pressure in the outlet chamber.
- the inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator corresponds at least to the inherent frequency of the switching valve.
- a high inherent frequency of this type of the switching valve can be achieved in particular if the switching piston is produced from a lightweight structural material.
- a lightweight structural material of this type may be, for example, a lightweight metal or else a plastics material, for example also a fiber-reinforced plastics material.
- a further advantageous form of the switching piston provides that it is formed as a hollow body, so that a high inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator can also be achieved in this way.
- FIG. 1 shows a diagrammatic representation of a refrigerating system according to the invention
- FIG. 2 shows a cross-section along line 2 - 2 through a refrigerant compressor of the refrigerating system according to the invention
- FIG. 3 shows a section through a switching valve integrated into a cylinder head in the open position of a valve body of the switching valve
- FIG. 4 shows a section similar to FIG. 3 in a closed position of the valve body of the switching valve
- FIG. 5 shows a diagrammatic representation of a switching interval comprising an opening interval and a closing interval
- FIG. 6 shows a diagrammatic representation of a behavior of the temperature of the evaporator in the refrigerating system when the compression of refrigerant is interrupted
- FIG. 7 shows a section similar to FIG. 3 through a second exemplary embodiment of a refrigerant compressor according to the invention.
- FIG. 8 shows a section similar to FIG. 4 through the second exemplary embodiment of a refrigerant compressor according to the invention.
- An exemplary embodiment of a refrigerating system according to the invention designated as a whole by 10 , comprises a refrigerant compressor 12 , from the high-pressure connection 14 of which a line 16 leads to a condenser, designated as a whole by 18 , in which the compressed refrigerant is condensed by removal of heat.
- liquid refrigerant flows in a line 20 to a collector 22 , in which the liquid refrigerant collects and from which the latter then flows via a line 28 to an expansion valve 30 for an evaporator 32 .
- the evaporated refrigerant flows via a line 34 to a low-pressure connection 36 of the refrigerant compressor 12 .
- the refrigerant compressor 12 is formed as a reciprocating piston compressor and comprises a compressor housing 40 , in which two banks of cylinders 42 a and 42 b , disposed in relation to each other in a V-shaped manner, are provided, each of which comprises at least one, in particular two or more, cylinder units 44 .
- Each of the cylinder units 44 is formed by a cylinder housing 46 , in which a piston 48 can be moved in an oscillating manner by the piston 48 being able to be driven by a connecting rod 50 , which for its part is mounted on an eccentric 52 of an eccentric shaft 54 , which is driven for example by an electric motor 55 .
- the cylinder housing 46 of each of the cylinder units 44 is closed off by a valve plate 56 , on which a cylinder head 58 is disposed.
- valve plate 56 preferably covers not only one cylinder housing 46 of a bank of cylinders 42 , but all the cylinder housings 46 of the respective bank of cylinders 42 , and in the same way the cylinder head 58 likewise reaches over all the cylinder housings 46 of the respective bank of cylinders 42 .
- the compressor housing 40 also comprises an inlet channel 60 , which is in connection with the low-pressure connection 36 and is, for example, integrated in the compressor housing 40 .
- a switching valve which is designated as a whole by 70 and serves the purpose of interrupting an inlet flow 74 of refrigerant passing from the inlet channel 60 through the valve plate 56 into the respective cylinder head 58 , to be precise into an inlet chamber 72 of the same, is associated with each bank of cylinders 42 .
- the inlet flow 74 has the possibility of entering via an inlet opening 76 , provided in the valve plate 56 , and an inlet valve 78 , provided on the valve plate 56 , into a cylinder chamber 80 , delimited by the respective piston 48 and the respective cylinder housing 46 as well as the valve plate 56 , in order to be compressed in said chamber by the oscillating movement of the piston 48 , so that an outlet flow 86 leaves the cylinder chamber 80 via an outlet opening 82 and an outlet valve 84 and enters into an outlet chamber 88 of the cylinder head 58 .
- the switching valve 70 is formed as a servo valve which is integrated in the cylinder head 58 and has a valve body 90 , with which an inflow opening 92 , provided in the valve plate 56 , of the inlet chamber 72 can be closed.
- the valve body 90 is also disposed on a switching piston 94 , which is guided in a switching cylinder housing 96 , so that the switching piston 94 can be moved in the direction of the valve plate 56 by pressure prevailing in a switching cylinder chamber 98 , to close the inflow opening 92 in said valve plate.
- a switching cylinder unit 100 which is formed by the switching cylinder housing 96 , the switching piston 94 and the switching cylinder chamber 98 and is integrated in the cylinder head 58 , is in this case controllable by means of a control valve 110 , which comprises an electromagnetically movable control piston 112 , with which a control valve seat 114 can be closed, the control piston 112 and the control valve seat 114 being provided for the purpose of interrupting or clearing a connection between a pressure channel 116 , leading to the outlet chamber 88 , and a pressure feed channel 118 , leading to the switching cylinder chamber 98 , for the switching cylinder 100 .
- a control valve 110 which comprises an electromagnetically movable control piston 112 , with which a control valve seat 114 can be closed, the control piston 112 and the control valve seat 114 being provided for the purpose of interrupting or clearing a connection between a pressure channel 116 , leading to the outlet chamber 88 , and a pressure feed channel 118 , leading to the switching cylinder chamber
- the switching cylinder chamber 98 is under the high pressure prevailing in the outlet chamber 88 and, consequently, the switching piston 94 moves in the direction of the valve plate 56 and presses the valve body 90 against the latter, in order to close the inflow opening 92 in the valve plate 56 .
- the force acting on the switching piston 94 as a result of the high pressure in the switching cylinder chamber 98 opposes the force of an elastic force accumulator 120 , which on the one hand is supported on the switching cylinder housing 96 and on the other hand acts on the switching piston 94 in such a way that the latter moves away from the valve plate 56 , and consequently moves the valve body 90 into a position clearing the inflow opening 92 .
- the switching piston 94 is provided with a pressure relieving channel 122 , which leads from an opening facing the switching cylinder chamber 98 to an outlet opening 124 , which is represented in FIG. 4 and, in the position of the valve body 90 and of the switching piston 94 that closes the inflow opening 92 , opens out into the inlet chamber 72 .
- the pressure relieving channel 124 has the effect in this case that, when there is an interruption of the connection between the high-pressure channel 116 and the pressure feed channel 118 , the pressure in the switching cylinder chamber 98 rapidly collapses, and consequently the switching piston 94 together with the valve body 90 move under the action of the elastic force accumulator 120 into a position clearing the inflow opening 92 , represented in FIG. 3 .
- the switching valve 70 can be activated by a control 130 , represented in FIG. 1 , in such a way that it closes and opens the switching valve 70 in continuously successive switching intervals SI, each of the switching intervals SI having an opening interval O, in which the valve body 90 in its clearing position allows the inlet flow 74 to pass through the inflow opening 92 , and a closing interval S, in which the valve body 90 , as represented in FIG. 4 , in its closing position blocks the flowing of the inlet flow 74 through the inflow opening 92 .
- the time period of the opening interval O and of the closing interval S can then be set variably in relation to each other in all part-load ranges, so that either the opening interval O is greater than the closing interval or vice versa.
- the opening interval O may extend substantially over the entire duration of the switching interval SI, while the closing interval S becomes as small as desired, or, conversely, the closing interval S may extend substantially over the entire duration of the switching interval SI, so that the opening interval O is as small as desired.
- the system is provided with a reaction inertia, so that, when there is an interruption of the suction removal of refrigerant from the evaporator 32 , the temperature T of the evaporator 32 does not rise immediately but instead, as represented in FIG. 6 , requires a time period Z to rise by a value D.
- the switching interval SI is chosen such that it is shorter than the time period Z that elapses before the temperature T of the evaporator 32 has risen from a temperature T A of the evaporator 32 by a value D of approximately 10%, even better approximately 5%, when there is a sudden interruption in the suction removal of refrigerant from the evaporator 32 and the feeding of medium under high pressure takes place at the high-pressure connection 14 .
- the time periods of the switching intervals SI usually lie around time periods which are shorter than approximately 10 seconds, even better shorter than approximately 2 seconds.
- the switching intervals are longer than approximately 0.02 seconds, even better longer than 0.05 seconds and preferably longer than 0.1 seconds.
- a preferred operating range provides switching intervals SI of a duration that lies between 0.1 and 10 seconds.
- the switching pistons 94 together with the valve bodies 90 and the elastic force accumulators 120 altogether have an inherent frequency which is higher than the frequency corresponding to the maximum switching intervals SI, so that the switching pistons 94 are capable of realizing the opening intervals O and the closing intervals S substantially without delay within the switching intervals SI.
- the inherent frequencies of the systems comprising the switching piston 94 , valve body 90 and elastic force accumulator 120 are preferably higher than the frequencies corresponding to the switching intervals SI by a factor of at least 5 or even better at least 10.
- the switching pistons 94 are made of a lightweight structural material, for example lightweight metal or plastics material, in order that small masses have to be moved.
- the switching pistons 94 ′ are formed as hollow bodies, in order to achieve a mass that is as small as possible, and consequently an inherent frequency that is as high as possible.
- the solution according to the invention provides, for example, a switching valve 70 of this type for each bank of cylinders, so that there is the possibility of correspondingly switching off the inlet flow for all the cylinder units 44 of a bank of cylinders 42 .
- a switching valve 70 of this type in such a way that it controls the inlet flow 74 to all the cylinder units 44 of the entire refrigerant compressor.
- control 130 controls all the cylinder units 44 with the same switching intervals.
- the control 130 is then capable when the refrigerant compressor 12 is operated in the full-load range of activating the switching valve 70 in such a way that the valve body 90 is constantly in the position clearing the inflow opening 92 , so that the inlet flow 74 can flow to all the cylinder units 44 of the respective bank of cylinders 42 .
- control 130 is capable of continuously setting any desired part load, to be precise in such a way that the time period of the opening interval O and the time period of the closing interval S, which add together to give the time period of the switching interval SI, are set variably in the desired ratio.
- the switching interval SI may be equal in all part-load ranges.
- the variation of the switching interval SI takes place in such a way that, at low rotational speed of the electric motor, the switching intervals SI are long and at high rotational speed of the electric motor the switching intervals are shorter.
- the advantage of the solution according to the invention can be seen in that, in the case of the reciprocating piston compressor, the power consumption is proportional to the mass throughput, and consequently, when there is a reduction in the mass throughput through successive opening intervals O and closing intervals S in the part-load range, there is the possibility of also reducing the power consumption of the reciprocating piston compressor.
- the solution according to the invention provides the possibility of controlling the mass throughput to implement the starting process of the refrigerant compressor 12 in such a way as to minimize the risks of boiling-out refrigerant.
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Abstract
In order to improve a refrigerant compressor for refrigerating systems comprising at least one cylinder unit, which has a cylinder housing and a piston which can move in an oscillating manner in the cylinder housing, a cylinder head, with an inlet chamber, flowed through by an inlet flow of the at least one cylinder unit, and with an outlet chamber, passed through by an outlet flow of the at least one cylinder unit, and a switching valve for interrupting the inlet flow in such a way that it can be operated in any desired part-load range, it is proposed that a control for activating the switching valve is provided, which control, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than a shortest time period after which a temperature of an evaporator in the operating refrigerating system has risen by approximately 10% during an interruption of the inlet flow.
Description
- This patent application claims the benefit of German Application No. 10 2005 016 433.1, filed Apr. 5, 2005, the teachings and disclosure of which are hereby incorporated in its entirety by reference thereto.
- The invention relates to a refrigerant compressor for refrigerating systems comprising at least one cylinder unit, which has a cylinder housing and a piston which can move in an oscillating manner in the cylinder housing, a cylinder head, with an inlet chamber, flowed through by an inlet flow of the at least one cylinder unit, and with an outlet chamber, passed through by an outlet flow of the at least one cylinder unit, and also a switching valve for interrupting the inlet flow.
- Refrigerant compressors of this type are known from the prior art; with these, the switching valve provides the possibility of permanently switching off or permanently switching on one or more cylinder units.
- With this solution, controlling the mass throughput is possible just on the basis of the ratio of the swept volume of the switched-off cylinder units and the swept volume of the operating cylinder units.
- It is therefore an object of the invention to improve a refrigerant compressor of the generic type in such a way that it can be operated in any desired part-load ranges.
- This object is achieved in the case of a refrigerant compressor of the type described at the beginning by providing a control for activating the switching valve which, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than a shortest time period after which a temperature of an evaporator in the operating refrigerating system has risen by approximately 10% during an interruption of the inlet flow.
- The advantage of the solution according to the invention can be seen in that it opens up the possibility of operating in particular a reciprocating piston compressor in a lower part-load range with any desired part load, since the mass flow to be compressed can be set steplessly and as desired by the ratio of the opening intervals and the closing intervals within each switching interval.
- In this case, time periods that are adequately short are chosen for the switching intervals, so that, on account of the inertia of the reaction of the refrigerating system according to the invention to the switching intervals, only insubstantial temperature fluctuations that do not impair precise regulation of the temperature occur in the evaporator of the refrigerating systems.
- As an alternative to the solution described above, a further exemplary embodiment of a refrigerant compressor of the type described at the beginning provides a control for activating the switching valve which, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than approximately 10 seconds.
- Limiting the duration of the switching intervals in such a manner likewise creates the possibility in a way according to the invention of operating the refrigerant compressor in a lower part-load range with a part load that can be set as desired, without pressure fluctuations which impair the quality of the regulation of the refrigerating system occurring in said system.
- It is even more advantageous in this respect if the switching intervals are shorter than approximately 2 seconds.
- To be able to operate the switching valves effectively, it is preferably provided that the switching intervals are longer than approximately 0.02 seconds.
- It is even more advantageous if the switching intervals are longer than 0.05 seconds and particularly advantageous if the switching intervals are longer than 0.1 seconds.
- It is particularly advantageous for switching the switching valve if the switching intervals correspond to a switching frequency which is less than an inherent or natural frequency of the switching valve.
- It is even better if the switching intervals correspond to a switching frequency which is less than an inherent or natural frequency of the switching valve by a factor of 5.
- In principle, with the control according to the invention it would be conceivable in the lower part-load range for example to switch off some of the cylinder units and operate only some of the cylinder units in the switching intervals.
- However, a particularly suitable solution provides that, in the lower part-load range, the control operates all the cylinder units of the refrigerant compressor in the switching intervals.
- Furthermore, it is conceivable also in the upper part-load range to switch off only some of the cylinder units and operate other cylinder units in the switching intervals.
- It is particularly advantageous, however, if the control operates all the cylinder units in the switching intervals in the entire part-load range.
- With regard to the time duration of the switching intervals, a wide variety of solution possibilities are conceivable. For instance, a variant that is particularly advantageous for reasons of simplicity provides that the control operates with switching intervals that are of a constant time.
- Another advantageous solution provides that the control varies the switching intervals on the basis of a rotational drive speed of the refrigerant compressor.
- With regard to the form of the switching valve, so far no further details have been provided.
- So it would be conceivable to form the switching valve in such a way that it acts on the inlet flow directly, for example under magnetic control.
- For reasons of the required high valve forces, however, it has proven to be advantageous if the switching valve is a servo valve.
- In particular, it is advantageous in this respect if the servo valve comprises a valve body which can be actuated by a pressure associated with the pressure in the outlet chamber.
- In order to ensure that the valve body does not automatically assume the end position brought about by the pressure in the outlet chamber, it is preferably provided that the valve body is acted upon by an elastic force accumulator acting counter to the effect of the pressure on the valve body.
- With regard to the actuation of the valve body by the pressure in the outlet chamber, a wide variety of structural solutions are conceivable. For example, solutions with membranes acted upon by the pressure in the outlet chamber or the like would be conceivable.
- A particularly suitable solution provides that the valve body is coupled to a switching piston which can be acted upon by a pressure associated with the pressure in the outlet chamber and is guided in a switching cylinder housing, and which then actuates the valve body.
- With regard to acting upon the switching piston, it has proven to be advantageous if the switching piston and the switching cylinder housing enclose a switching cylinder chamber and if the pressure in the switching cylinder chamber is controllable.
- Furthermore, it is favorable for structural reasons if the valve body and the switching piston form a unit which is guided in the switching cylinder housing.
- Furthermore, it is advantageous in the case of a servo valve of this type if it comprises a control valve which can be activated by the control.
- A control valve of this type is formed for example as a rapidly responding, electrically activatable solenoid valve or similarly constructed valve.
- For operating the servo valve, it is provided in the case of an advantageous exemplary embodiment that the control valve opens or closes a connecting channel between the control cylinder chamber and the outlet chamber, so that, in a simple manner, there is the possibility of acting upon the switching piston with medium under the pressure in the outlet chamber.
- In the case of a servo valve of this type, to achieve an inherent frequency that is as high as possible, and consequently a short switching time, it is preferably provided that the inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator corresponds at least to the inherent frequency of the switching valve.
- A high inherent frequency of this type of the switching valve can be achieved in particular if the switching piston is produced from a lightweight structural material.
- A lightweight structural material of this type may be, for example, a lightweight metal or else a plastics material, for example also a fiber-reinforced plastics material.
- A further advantageous form of the switching piston provides that it is formed as a hollow body, so that a high inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator can also be achieved in this way.
- Further features and advantages of the invention are the subject of the description which follows and the representation of some exemplary embodiments in the drawing.
-
FIG. 1 shows a diagrammatic representation of a refrigerating system according to the invention; -
FIG. 2 shows a cross-section along line 2-2 through a refrigerant compressor of the refrigerating system according to the invention; -
FIG. 3 shows a section through a switching valve integrated into a cylinder head in the open position of a valve body of the switching valve; -
FIG. 4 shows a section similar toFIG. 3 in a closed position of the valve body of the switching valve; -
FIG. 5 shows a diagrammatic representation of a switching interval comprising an opening interval and a closing interval; -
FIG. 6 shows a diagrammatic representation of a behavior of the temperature of the evaporator in the refrigerating system when the compression of refrigerant is interrupted; -
FIG. 7 shows a section similar toFIG. 3 through a second exemplary embodiment of a refrigerant compressor according to the invention and -
FIG. 8 shows a section similar toFIG. 4 through the second exemplary embodiment of a refrigerant compressor according to the invention. - An exemplary embodiment of a refrigerating system according to the invention, designated as a whole by 10, comprises a
refrigerant compressor 12, from the high-pressure connection 14 of which aline 16 leads to a condenser, designated as a whole by 18, in which the compressed refrigerant is condensed by removal of heat. - From the
condenser 18, liquid refrigerant flows in aline 20 to acollector 22, in which the liquid refrigerant collects and from which the latter then flows via aline 28 to anexpansion valve 30 for anevaporator 32. - After flowing through the
evaporator 32, the evaporated refrigerant flows via aline 34 to a low-pressure connection 36 of therefrigerant compressor 12. - As represented in
FIG. 2 , therefrigerant compressor 12 according to the invention is formed as a reciprocating piston compressor and comprises acompressor housing 40, in which two banks ofcylinders cylinder units 44. - Each of the
cylinder units 44 is formed by acylinder housing 46, in which apiston 48 can be moved in an oscillating manner by thepiston 48 being able to be driven by a connectingrod 50, which for its part is mounted on an eccentric 52 of aneccentric shaft 54, which is driven for example by anelectric motor 55. - The
cylinder housing 46 of each of thecylinder units 44 is closed off by avalve plate 56, on which acylinder head 58 is disposed. - In this case, the
valve plate 56 preferably covers not only one cylinder housing 46 of a bank of cylinders 42, but all thecylinder housings 46 of the respective bank of cylinders 42, and in the same way thecylinder head 58 likewise reaches over all thecylinder housings 46 of the respective bank of cylinders 42. - The
compressor housing 40 also comprises aninlet channel 60, which is in connection with the low-pressure connection 36 and is, for example, integrated in thecompressor housing 40. - As shown enlarged in
FIG. 3 , a switching valve, which is designated as a whole by 70 and serves the purpose of interrupting aninlet flow 74 of refrigerant passing from theinlet channel 60 through thevalve plate 56 into therespective cylinder head 58, to be precise into aninlet chamber 72 of the same, is associated with each bank of cylinders 42. - If the
switching valve 70 is open, theinlet flow 74 has the possibility of entering via aninlet opening 76, provided in thevalve plate 56, and aninlet valve 78, provided on thevalve plate 56, into acylinder chamber 80, delimited by therespective piston 48 and therespective cylinder housing 46 as well as thevalve plate 56, in order to be compressed in said chamber by the oscillating movement of thepiston 48, so that an outlet flow 86 leaves thecylinder chamber 80 via an outlet opening 82 and anoutlet valve 84 and enters into anoutlet chamber 88 of thecylinder head 58. - The
switching valve 70 is formed as a servo valve which is integrated in thecylinder head 58 and has avalve body 90, with which aninflow opening 92, provided in thevalve plate 56, of theinlet chamber 72 can be closed. - The
valve body 90 is also disposed on aswitching piston 94, which is guided in a switchingcylinder housing 96, so that theswitching piston 94 can be moved in the direction of thevalve plate 56 by pressure prevailing in aswitching cylinder chamber 98, to close theinflow opening 92 in said valve plate. - A
switching cylinder unit 100, which is formed by the switchingcylinder housing 96, theswitching piston 94 and the switchingcylinder chamber 98 and is integrated in thecylinder head 58, is in this case controllable by means of acontrol valve 110, which comprises an electromagneticallymovable control piston 112, with which acontrol valve seat 114 can be closed, thecontrol piston 112 and thecontrol valve seat 114 being provided for the purpose of interrupting or clearing a connection between apressure channel 116, leading to theoutlet chamber 88, and apressure feed channel 118, leading to the switchingcylinder chamber 98, for theswitching cylinder 100. - If the connection between the high-
pressure channel 116 and thepressure feed channel 118 is cleared, the switchingcylinder chamber 98 is under the high pressure prevailing in theoutlet chamber 88 and, consequently, theswitching piston 94 moves in the direction of thevalve plate 56 and presses thevalve body 90 against the latter, in order to close theinflow opening 92 in thevalve plate 56. - In this case, the force acting on the
switching piston 94 as a result of the high pressure in the switchingcylinder chamber 98 opposes the force of anelastic force accumulator 120, which on the one hand is supported on theswitching cylinder housing 96 and on the other hand acts on theswitching piston 94 in such a way that the latter moves away from thevalve plate 56, and consequently moves thevalve body 90 into a position clearing theinflow opening 92. - In particular, the
switching piston 94 is provided with apressure relieving channel 122, which leads from an opening facing the switchingcylinder chamber 98 to anoutlet opening 124, which is represented inFIG. 4 and, in the position of thevalve body 90 and of theswitching piston 94 that closes theinflow opening 92, opens out into theinlet chamber 72. Thepressure relieving channel 124 has the effect in this case that, when there is an interruption of the connection between the high-pressure channel 116 and thepressure feed channel 118, the pressure in the switchingcylinder chamber 98 rapidly collapses, and consequently theswitching piston 94 together with thevalve body 90 move under the action of theelastic force accumulator 120 into a position clearing theinflow opening 92, represented inFIG. 3 . - The switching
valve 70 can be activated by acontrol 130, represented inFIG. 1 , in such a way that it closes and opens the switchingvalve 70 in continuously successive switching intervals SI, each of the switching intervals SI having an opening interval O, in which thevalve body 90 in its clearing position allows theinlet flow 74 to pass through theinflow opening 92, and a closing interval S, in which thevalve body 90, as represented inFIG. 4 , in its closing position blocks the flowing of theinlet flow 74 through theinflow opening 92. - Within the duration of the respective switching interval SI, the time period of the opening interval O and of the closing interval S can then be set variably in relation to each other in all part-load ranges, so that either the opening interval O is greater than the closing interval or vice versa.
- In the extreme case, the opening interval O may extend substantially over the entire duration of the switching interval SI, while the closing interval S becomes as small as desired, or, conversely, the closing interval S may extend substantially over the entire duration of the switching interval SI, so that the opening interval O is as small as desired.
- Since, in the refrigerating
system 10 according to the invention, evaporation of liquid refrigerant generally takes place constantly via theexpansion valve 30, an interruption of the compression of refrigerant by therefrigerant compressor 12 leads to a rise of the temperature T in theevaporator 32. - However, the system is provided with a reaction inertia, so that, when there is an interruption of the suction removal of refrigerant from the
evaporator 32, the temperature T of theevaporator 32 does not rise immediately but instead, as represented inFIG. 6 , requires a time period Z to rise by a value D. - As long as the value D lies around values less than 10% of an initial temperature TA of the evaporator, these fluctuations are irrelevant to the function of the refrigerating system according to the invention.
- For this reason, the switching interval SI is chosen such that it is shorter than the time period Z that elapses before the temperature T of the
evaporator 32 has risen from a temperature TA of theevaporator 32 by a value D of approximately 10%, even better approximately 5%, when there is a sudden interruption in the suction removal of refrigerant from theevaporator 32 and the feeding of medium under high pressure takes place at the high-pressure connection 14. - This ensures that the opening intervals O and the closing intervals S within the respective switching interval SI have no significant effect on the function of the refrigerating system and merely lead to slight temperature fluctuations of the
evaporator 32 of the refrigerating system according to the invention. - The time periods of the switching intervals SI usually lie around time periods which are shorter than approximately 10 seconds, even better shorter than approximately 2 seconds.
- On the other hand, in order to ensure adequate opening intervals O, the switching intervals are longer than approximately 0.02 seconds, even better longer than 0.05 seconds and preferably longer than 0.1 seconds.
- A preferred operating range provides switching intervals SI of a duration that lies between 0.1 and 10 seconds.
- To ensure such shorter time intervals SI, it is preferably provided that the switching
pistons 94 together with thevalve bodies 90 and theelastic force accumulators 120 altogether have an inherent frequency which is higher than the frequency corresponding to the maximum switching intervals SI, so that the switchingpistons 94 are capable of realizing the opening intervals O and the closing intervals S substantially without delay within the switching intervals SI. - The inherent frequencies of the systems comprising the
switching piston 94,valve body 90 andelastic force accumulator 120 are preferably higher than the frequencies corresponding to the switching intervals SI by a factor of at least 5 or even better at least 10. - To realize this, it is suitably provided that the switching
pistons 94 are made of a lightweight structural material, for example lightweight metal or plastics material, in order that small masses have to be moved. - In the case of a second exemplary embodiment of a refrigerant compressor according to the invention, represented in
FIGS. 7 and 8 , the switchingpistons 94′ are formed as hollow bodies, in order to achieve a mass that is as small as possible, and consequently an inherent frequency that is as high as possible. - The solution according to the invention provides, for example, a switching
valve 70 of this type for each bank of cylinders, so that there is the possibility of correspondingly switching off the inlet flow for all thecylinder units 44 of a bank of cylinders 42. - However, it is also conceivable to dispose a switching
valve 70 of this type in such a way that it controls theinlet flow 74 to all thecylinder units 44 of the entire refrigerant compressor. - In the case of an advantageous solution, at least in a lower part-load range, that is to say in a range between approximately 1% and approximately 30% of the maximum mass flow, the
control 130 controls all thecylinder units 44 with the same switching intervals. - However, even in higher part-load ranges, for example in an upper part-load range between approximately 30% and 100% of the maximum mass flow, it is advantageous to operate all the
cylinder units 44 with the same switching intervals in order to avoid balancing problems of the reciprocating piston compressor that occur ifcylinder units 44 are completely switched off. - The
control 130 is then capable when therefrigerant compressor 12 is operated in the full-load range of activating the switchingvalve 70 in such a way that thevalve body 90 is constantly in the position clearing theinflow opening 92, so that theinlet flow 74 can flow to all thecylinder units 44 of the respective bank of cylinders 42. - In this case, the maximum mass flow of refrigerant is compressed to high pressure H.
- There is also the possibility of activating the switching
valve 70 in a zero-load range in such a way that thevalve body 90 is constantly in its position closing theinflow opening 92. In this case, substantially no mass flow of refrigerant is compressed. Only the mass flow flowing through thepressure channel 116 and the pressure of thechannel 118 and also thepressure relieving channel 122 is compressed. - In the part-load range, the
control 130 is capable of continuously setting any desired part load, to be precise in such a way that the time period of the opening interval O and the time period of the closing interval S, which add together to give the time period of the switching interval SI, are set variably in the desired ratio. - In this case, the switching interval SI may be equal in all part-load ranges.
- However, it is also conceivable to vary the switching interval SI either proportionally or in individual steps dependent on the rotational speed of the
eccentric shaft 54, and consequently of theelectric motor 55. - For example, the variation of the switching interval SI takes place in such a way that, at low rotational speed of the electric motor, the switching intervals SI are long and at high rotational speed of the electric motor the switching intervals are shorter.
- The advantage of the solution according to the invention can be seen in that, in the case of the reciprocating piston compressor, the power consumption is proportional to the mass throughput, and consequently, when there is a reduction in the mass throughput through successive opening intervals O and closing intervals S in the part-load range, there is the possibility of also reducing the power consumption of the reciprocating piston compressor.
- Furthermore, the solution according to the invention provides the possibility of controlling the mass throughput to implement the starting process of the
refrigerant compressor 12 in such a way as to minimize the risks of boiling-out refrigerant.
Claims (23)
1. Refrigerant compressor for refrigerating systems comprising
at least one cylinder unit, which has a cylinder housing and a piston which can move in an oscillating manner in the cylinder housing, a cylinder head, with an inlet chamber, flowed through by an inlet flow of the at least one cylinder unit, and with an outlet chamber, passed through by an outlet flow of the at least one cylinder unit, and a switching valve for interrupting the inlet flow,
a control for activating the switching valve, which control, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals, respectively comprising an opening interval and a closing interval of the switching valve, which are shorter than a shortest time period after which a temperature of an evaporator in the operating refrigerating system has risen by approximately 10% during an interruption of the inlet flow.
2. Refrigerant compressor for refrigerating systems comprising
at least one cylinder unit, which has a cylinder housing and a piston which can move in an oscillating manner in the cylinder housing, a cylinder head, with an inlet chamber, flowed through by an inlet flow of the at least one cylinder unit, and with an outlet chamber, passed through by an outlet flow of the at least one cylinder unit, and a switching valve for interrupting the inlet flow,
a control for activating the switching valve, which control, for operating the refrigerant compressor in a lower part-load range, operates the switching valve in successive switching intervals which are shorter than approximately 10 seconds.
3. Refrigerant compressor according to claim 2 , wherein the switching intervals are shorter than approximately 2 seconds.
4. Refrigerant compressor according to claim 1 , wherein the switching intervals are longer than approximately 0.02 seconds.
5. Refrigerant compressor according to claim 4 , wherein the switching intervals are longer than approximately 0.05 seconds.
6. Refrigerant compressor according to claim 5 , wherein the switching intervals are longer than approximately 0.1 seconds.
7. Refrigerant compressor according to claim 1 , wherein the switching intervals correspond to a switching frequency which is less than an inherent frequency of the switching valve.
8. Refrigerant compressor according to claim 7 , wherein the switching intervals correspond to a switching frequency which is less than an inherent frequency of the switching valve by more than a factor of 5.
9. Refrigerant compressor according to claim 1 , wherein in the lower part-load range, the control operates all the cylinder units in the switching intervals.
10. Refrigerant compressor according to claim 9 , wherein the control operates all the cylinder units in the switching intervals in the entire part-load range.
11. Refrigerant compressor according to claim 1 , wherein the control operates with switching intervals that are of a constant time.
12. Refrigerant compressor according to claim 1 , wherein the control varies the switching intervals on the basis of a rotational drive speed of the refrigerant compressor.
13. Refrigerant compressor according to claim 1 , wherein the switching valve is a servo valve.
14. Refrigerant compressor according to claim 13 , wherein the servo valve comprises a valve body which can be actuated by a pressure associated with the pressure in the outlet chamber.
15. Refrigerant compressor according to claim 14 , wherein the valve body is acted upon by an elastic force accumulator acting counter to the effect of the pressure on the valve body.
16. Refrigerant compressor according to claim 14 , wherein the valve body is coupled to a switching piston which can be acted upon by a pressure associated with the pressure in the outlet chamber and is guided in a switching cylinder housing.
17. Refrigerant compressor according to claim 14 , wherein the switching piston and the switching cylinder housing enclose a switching cylinder chamber and in that the pressure in the switching cylinder chamber is controllable.
18. Refrigerant compressor according to claim 14 , wherein the valve body and the switching piston form a unit which is guided in the switching cylinder housing.
19. Refrigerant compressor according to claim 13 , wherein the servo valve comprises a control valve which can be activated by the control.
20. Refrigerant compressor according to claim 19 , wherein the control valve opens or closes the connecting channel between the switching cylinder chamber and the outlet chamber.
21. Refrigerant compressor according to claim 15 , wherein the inherent frequency of the unit comprising the switching piston, valve body and elastic force accumulator corresponds at least to the inherent frequency of the switching valve.
22. Refrigerant compressor according to claim 14 , wherein the switching piston is produced from a lightweight structural material.
23. Refrigerant compressor according to claim 14 , wherein the switching piston is formed as a hollow body.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102005016433.1 | 2005-04-05 | ||
DE102005016433A DE102005016433A1 (en) | 2005-04-05 | 2005-04-05 | Refrigerant compressor |
Publications (1)
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US20060218959A1 true US20060218959A1 (en) | 2006-10-05 |
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US11/393,215 Abandoned US20060218959A1 (en) | 2005-04-05 | 2006-03-30 | Refrigerant compressor |
Country Status (10)
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US (1) | US20060218959A1 (en) |
EP (1) | EP1710435B2 (en) |
CN (1) | CN100523671C (en) |
AT (1) | ATE371111T1 (en) |
DE (2) | DE102005016433A1 (en) |
DK (1) | DK1710435T3 (en) |
ES (1) | ES2290930T5 (en) |
PL (1) | PL1710435T3 (en) |
PT (1) | PT1710435E (en) |
SI (1) | SI1710435T1 (en) |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090028723A1 (en) * | 2007-07-23 | 2009-01-29 | Wallis Frank S | Capacity modulation system for compressor and method |
US7654098B2 (en) | 1995-06-07 | 2010-02-02 | Emerson Climate Technologies, Inc. | Cooling system with variable capacity control |
US20100189581A1 (en) * | 2009-01-27 | 2010-07-29 | Wallis Frank S | Unloader system and method for a compressor |
WO2011011221A2 (en) | 2009-07-20 | 2011-01-27 | Carrier Corporation | Suction cutoff unloader valve for compressor capacity control |
US20130139535A1 (en) * | 2011-12-06 | 2013-06-06 | Terry Nares | Control for Compressor Unloading System |
USRE44636E1 (en) | 1997-09-29 | 2013-12-10 | Emerson Climate Technologies, Inc. | Compressor capacity modulation |
RU2528791C2 (en) * | 2008-08-12 | 2014-09-20 | Кэрие Корпорейшн | Separate pulse valve for compressor cylinder |
WO2014167542A1 (en) | 2013-04-11 | 2014-10-16 | Frascold S.P.A. | Compressor for a refrigerating plant and refrigerating plant comprising said compressor |
US20150316304A1 (en) * | 2013-02-13 | 2015-11-05 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system comprising a motor, and a compressor of a refrigeration system |
EP2955377A4 (en) * | 2013-02-08 | 2017-02-15 | Hitachi Industrial Equipment Systems Co., Ltd. | Fluid compression system and control device therefor |
WO2021124087A1 (en) * | 2019-12-17 | 2021-06-24 | Officine Mario Dorin S.P.A. | Multi-cylinder reciprocating compressor |
US11137170B2 (en) | 2016-11-11 | 2021-10-05 | Carrier Corporation | Heat pump system and start up control method thereof |
US20220381236A1 (en) * | 2020-02-14 | 2022-12-01 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012107183B4 (en) | 2012-08-06 | 2016-08-04 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system and a refrigeration system |
WO2014023694A2 (en) | 2012-08-06 | 2014-02-13 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system, and refrigeration system |
JP5984784B2 (en) * | 2013-11-19 | 2016-09-06 | 三菱電機株式会社 | Hot / cold water air conditioning system |
DE102020118740A1 (en) * | 2020-07-15 | 2022-01-20 | Bitzer Kühlmaschinenbau Gmbh | refrigerant compressor |
DE102021117724A1 (en) * | 2021-07-08 | 2023-01-12 | Bitzer Kühlmaschinenbau Gmbh | refrigerant compressor group |
Citations (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4149827A (en) * | 1976-04-27 | 1979-04-17 | Hofmann Jr Rudolf | Method and apparatus for controlling operation of a compressor |
US4878818A (en) * | 1988-07-05 | 1989-11-07 | Carrier Corporation | Common compression zone access ports for positive displacement compressor |
US4909043A (en) * | 1987-10-26 | 1990-03-20 | Diesel Kiki Co., Ltd. | Air conditioning control system for automotive vehicles |
US5189886A (en) * | 1987-09-22 | 1993-03-02 | Sanden Corporation | Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism |
US5507316A (en) * | 1994-09-15 | 1996-04-16 | Eaton Corporation | Engine hydraulic valve actuator spool valve |
US5540061A (en) * | 1992-01-09 | 1996-07-30 | Hitachi, Ltd. | Refrigerator |
US6047556A (en) * | 1997-12-08 | 2000-04-11 | Carrier Corporation | Pulsed flow for capacity control |
US6047557A (en) * | 1995-06-07 | 2000-04-11 | Copeland Corporation | Adaptive control for a refrigeration system using pulse width modulated duty cycle scroll compressor |
US6206652B1 (en) * | 1998-08-25 | 2001-03-27 | Copeland Corporation | Compressor capacity modulation |
US6401472B2 (en) * | 1999-04-22 | 2002-06-11 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor apparatus |
US20020195151A1 (en) * | 2001-05-24 | 2002-12-26 | Erickson Bradley C. | Pulse-width modulated solenoid valve including axial stop spool valve |
US20030070441A1 (en) * | 2000-06-07 | 2003-04-17 | Joong-Ki Moon | Control system of degree of superheat of air conditioner and control method thereof |
US20040079096A1 (en) * | 2002-10-25 | 2004-04-29 | Satoshi Itoh | Vehicle air conditioning system |
US20040093881A1 (en) * | 2001-02-16 | 2004-05-20 | Jong-Youb Kim | Air conditioner and method of controlling the same |
US20040231348A1 (en) * | 2003-05-16 | 2004-11-25 | Masakazu Murase | Apparatus for variable displacement type compressor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4212162C2 (en) * | 1992-04-10 | 1994-02-17 | Ilka Maschinenfabrik Halle Gmb | Device for cooling the electric motor of a semi-hermetic refrigerant compressor |
DE112004002149D2 (en) * | 2003-09-02 | 2006-07-13 | Luk Fahrzeug Hydraulik | Compressor or air conditioning |
-
2005
- 2005-04-05 DE DE102005016433A patent/DE102005016433A1/en not_active Ceased
-
2006
- 2006-03-23 DE DE502006000063T patent/DE502006000063D1/en active Active
- 2006-03-23 EP EP06005929.2A patent/EP1710435B2/en active Active
- 2006-03-23 DK DK06005929T patent/DK1710435T3/en active
- 2006-03-23 ES ES06005929T patent/ES2290930T5/en active Active
- 2006-03-23 PT PT06005929T patent/PT1710435E/en unknown
- 2006-03-23 PL PL06005929T patent/PL1710435T3/en unknown
- 2006-03-23 AT AT06005929T patent/ATE371111T1/en not_active IP Right Cessation
- 2006-03-23 SI SI200630009T patent/SI1710435T1/en unknown
- 2006-03-30 US US11/393,215 patent/US20060218959A1/en not_active Abandoned
- 2006-04-05 CN CNB2006100732185A patent/CN100523671C/en not_active Ceased
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4149827A (en) * | 1976-04-27 | 1979-04-17 | Hofmann Jr Rudolf | Method and apparatus for controlling operation of a compressor |
US5189886A (en) * | 1987-09-22 | 1993-03-02 | Sanden Corporation | Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism |
US4909043A (en) * | 1987-10-26 | 1990-03-20 | Diesel Kiki Co., Ltd. | Air conditioning control system for automotive vehicles |
US4878818A (en) * | 1988-07-05 | 1989-11-07 | Carrier Corporation | Common compression zone access ports for positive displacement compressor |
US5540061A (en) * | 1992-01-09 | 1996-07-30 | Hitachi, Ltd. | Refrigerator |
US5507316A (en) * | 1994-09-15 | 1996-04-16 | Eaton Corporation | Engine hydraulic valve actuator spool valve |
US6499305B2 (en) * | 1995-06-07 | 2002-12-31 | Copeland Corporation | Adaptive control for a refrigeration system using pulse width modulated duty cycle scroll compressor |
US6047557A (en) * | 1995-06-07 | 2000-04-11 | Copeland Corporation | Adaptive control for a refrigeration system using pulse width modulated duty cycle scroll compressor |
US6047556A (en) * | 1997-12-08 | 2000-04-11 | Carrier Corporation | Pulsed flow for capacity control |
US6206652B1 (en) * | 1998-08-25 | 2001-03-27 | Copeland Corporation | Compressor capacity modulation |
US6401472B2 (en) * | 1999-04-22 | 2002-06-11 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor apparatus |
US20030070441A1 (en) * | 2000-06-07 | 2003-04-17 | Joong-Ki Moon | Control system of degree of superheat of air conditioner and control method thereof |
US20040093881A1 (en) * | 2001-02-16 | 2004-05-20 | Jong-Youb Kim | Air conditioner and method of controlling the same |
US20020195151A1 (en) * | 2001-05-24 | 2002-12-26 | Erickson Bradley C. | Pulse-width modulated solenoid valve including axial stop spool valve |
US20040079096A1 (en) * | 2002-10-25 | 2004-04-29 | Satoshi Itoh | Vehicle air conditioning system |
US20040231348A1 (en) * | 2003-05-16 | 2004-11-25 | Masakazu Murase | Apparatus for variable displacement type compressor |
Cited By (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7654098B2 (en) | 1995-06-07 | 2010-02-02 | Emerson Climate Technologies, Inc. | Cooling system with variable capacity control |
USRE44636E1 (en) | 1997-09-29 | 2013-12-10 | Emerson Climate Technologies, Inc. | Compressor capacity modulation |
US20090028723A1 (en) * | 2007-07-23 | 2009-01-29 | Wallis Frank S | Capacity modulation system for compressor and method |
US8157538B2 (en) * | 2007-07-23 | 2012-04-17 | Emerson Climate Technologies, Inc. | Capacity modulation system for compressor and method |
US8807961B2 (en) | 2007-07-23 | 2014-08-19 | Emerson Climate Technologies, Inc. | Capacity modulation system for compressor and method |
RU2528791C2 (en) * | 2008-08-12 | 2014-09-20 | Кэрие Корпорейшн | Separate pulse valve for compressor cylinder |
US20100189581A1 (en) * | 2009-01-27 | 2010-07-29 | Wallis Frank S | Unloader system and method for a compressor |
US8308455B2 (en) | 2009-01-27 | 2012-11-13 | Emerson Climate Technologies, Inc. | Unloader system and method for a compressor |
US20120192583A1 (en) * | 2009-07-20 | 2012-08-02 | Carrier Corporation | Suction Cutoff Unloader Valve For Compressor Capacity Control |
WO2011011221A2 (en) | 2009-07-20 | 2011-01-27 | Carrier Corporation | Suction cutoff unloader valve for compressor capacity control |
CN102472269A (en) * | 2009-07-20 | 2012-05-23 | 开利公司 | Suction cutoff unloader valve for compressor capacity control |
US20130139535A1 (en) * | 2011-12-06 | 2013-06-06 | Terry Nares | Control for Compressor Unloading System |
US10378533B2 (en) * | 2011-12-06 | 2019-08-13 | Bitzer Us, Inc. | Control for compressor unloading system |
EP3196465A1 (en) * | 2011-12-06 | 2017-07-26 | Bitzer Us, Inc. | Control for compressor unloading system |
US10514026B2 (en) | 2013-02-08 | 2019-12-24 | Hitachi Industrial Equipment Systems Co., Ltd. | Fluid compression system and control device therefor |
EP2955377A4 (en) * | 2013-02-08 | 2017-02-15 | Hitachi Industrial Equipment Systems Co., Ltd. | Fluid compression system and control device therefor |
US20150316304A1 (en) * | 2013-02-13 | 2015-11-05 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system comprising a motor, and a compressor of a refrigeration system |
US9982928B2 (en) * | 2013-02-13 | 2018-05-29 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system comprising a motor, and a compressor of a refrigeration system |
WO2014167542A1 (en) | 2013-04-11 | 2014-10-16 | Frascold S.P.A. | Compressor for a refrigerating plant and refrigerating plant comprising said compressor |
US10228173B2 (en) * | 2013-04-11 | 2019-03-12 | Frascold S.P.A. | Compressor for a refrigerating plant and refrigerating plant comprising said compressor |
US20160061503A1 (en) * | 2013-04-11 | 2016-03-03 | Frascold S.P.A. | Compressor for a refrigerating plant and refrigerating plant comprising said compressor |
US11137170B2 (en) | 2016-11-11 | 2021-10-05 | Carrier Corporation | Heat pump system and start up control method thereof |
WO2021124087A1 (en) * | 2019-12-17 | 2021-06-24 | Officine Mario Dorin S.P.A. | Multi-cylinder reciprocating compressor |
CN114981540A (en) * | 2019-12-17 | 2022-08-30 | 马里奥·多林工作坊股份公司 | Multi-cylinder reciprocating compressor |
US20220381236A1 (en) * | 2020-02-14 | 2022-12-01 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor |
Also Published As
Publication number | Publication date |
---|---|
DE102005016433A1 (en) | 2006-10-12 |
EP1710435A1 (en) | 2006-10-11 |
ES2290930T3 (en) | 2008-02-16 |
EP1710435B1 (en) | 2007-08-22 |
DK1710435T3 (en) | 2008-01-28 |
ES2290930T5 (en) | 2023-11-20 |
PT1710435E (en) | 2007-09-24 |
CN1847757A (en) | 2006-10-18 |
PL1710435T3 (en) | 2008-01-31 |
SI1710435T1 (en) | 2008-02-29 |
ATE371111T1 (en) | 2007-09-15 |
DE502006000063D1 (en) | 2007-10-04 |
EP1710435B2 (en) | 2023-06-07 |
CN100523671C (en) | 2009-08-05 |
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Owner name: BITZER KUEHLMASCHINENBAU GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SANDKOETTER, WOLFGANG;REEL/FRAME:017549/0627 Effective date: 20060320 |
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