EP4276311A2 - Compresseur frigorifique semi-hermétique - Google Patents

Compresseur frigorifique semi-hermétique Download PDF

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Publication number
EP4276311A2
EP4276311A2 EP23195632.7A EP23195632A EP4276311A2 EP 4276311 A2 EP4276311 A2 EP 4276311A2 EP 23195632 A EP23195632 A EP 23195632A EP 4276311 A2 EP4276311 A2 EP 4276311A2
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
control unit
electric motor
power control
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
EP23195632.7A
Other languages
German (de)
English (en)
Other versions
EP4276311A3 (fr
Inventor
Rainer Große-Kracht
Hermann Renz
Eduardo Martin
Jens MANNEWITZ
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to EP23195632.7A priority Critical patent/EP4276311A3/fr
Publication of EP4276311A2 publication Critical patent/EP4276311A2/fr
Publication of EP4276311A3 publication Critical patent/EP4276311A3/fr
Pending legal-status Critical Current

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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
    • 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
    • F04B35/04—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 electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • 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
    • 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
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/18—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use for specific elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • 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
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B49/24—Bypassing
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/007—Cylinder heads
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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

Definitions

  • the invention relates to a semi-hermetic refrigerant compressor, comprising a reciprocating compressor and an electric motor, an overall housing which has a motor housing section for the electric motor and a compressor housing section for the reciprocating compressor, a suction-side refrigerant path leading from a suction connection on the overall housing to an inlet chamber of the reciprocating compressor, and one from an outlet chamber of the reciprocating compressor to a pressure connection on the entire housing leading to the pressure-side refrigerant path, wherein in the compressor housing section at least one cylinder of the reciprocating compressor is provided, which has a piston movable in a cylinder bore formed in the compressor housing section, a valve plate closing the cylinder bore and a valve plate which overlaps the valve plate and forms part of the compressor housing section Has cylinder head.
  • Such semi-hermetic refrigerant compressors are known from the prior art.
  • a semi-hermetic refrigerant compressor has the overall housing as an outer housing, with the electric motor in particular being arranged in a refrigerant atmosphere.
  • a semi-hermetic refrigerant compressor is not provided with an outer encapsulation that completely encloses the reciprocating piston compressor and the electric motor, but that at least one compressor housing forming the cylinder housing itself represents the outer housing.
  • This object is achieved according to the invention in a semi-hermetic refrigerant compressor in that the refrigerant compressor is provided with an externally controllable or controlled mechanical power control unit.
  • Such an externally controlled power control unit creates the possibility of controlling the compressor delivery capacity of the semi-hermetic refrigerant compressor by means of the mechanical power control unit without a frequency converter for the electric motor, which is inexpensive and efficient, and in addition, in particular, it opens up the possibility of reducing the mechanical loads on the reciprocating compressor .
  • the mechanical power control unit connects the outlet-side refrigerant path with the inlet-side refrigerant path for power reduction in at least one cylinder.
  • This solution has the advantage that the mechanical load on the components of the reciprocating compressor is low when there is a reduction in performance, since the refrigerant flows back from the outlet side to the inlet side at a pressure level that is close to the inlet side and there are no large pressure fluctuations or even Pressure peaks and temperature peaks occur in the reciprocating compressor, which in particular also reduce the efficiency when power is reduced.
  • An advantageous solution provides for the mechanical power control unit to be arranged on the cylinder head, which has the advantage that the mechanical power control unit can easily interact with at least one of the cylinders.
  • the mechanical power control unit is at least partially integrated into the at least one cylinder head.
  • the mechanical power control unit connects an outlet chamber in the cylinder head to an inlet chamber in the cylinder head by means of a connecting channel to reduce power.
  • the connecting channel is arranged integrated into the cylinder head, so that the space required for the interaction of the power control unit with the inlet chamber and the outlet chamber can also be optimized.
  • the outlet chamber in the cylinder head is arranged directly adjacent to at least one outlet opening for the respective cylinder in the valve plate and thus in particular the outlet chamber also directly adjoins the valve plate and the outlet opening, in particular with the exhaust valve.
  • the inlet chamber in the cylinder head is arranged immediately adjacent to an inlet opening for the respective cylinder in the valve plate, so that the inlet chamber also directly adjoins the valve plate and the inlet opening.
  • a particularly advantageous solution provides that the mechanical power control unit has a closure piston for closing the connecting channel.
  • Such a closure piston creates the possibility of opening or closing the connecting channel, in particular with the shortest possible reaction time.
  • the closure piston is preferably sealed with a piston ring in a guide bore, in particular in the cylinder head.
  • the closing piston can be placed on a sealing seat for closing the connecting channel, which extends enclosing the connecting channel, so that when the closing piston is placed on the sealing seat, the connecting channel is interrupted, while when the closing piston is lifted off the compression seat, the connecting channel is opened again .
  • a sealing area of the closure piston that can be placed on the sealing seat is made of a metal that has a lower hardness than a metal from which the sealing seat is made, or vice versa.
  • the sealing seat can be arranged in a variety of ways.
  • seal seat is arranged in a wall section of the cylinder head that separates the inlet chamber from the outlet chamber.
  • the sealing seat can either be designed as part of the wall section or the sealing seat is formed by a component inserted into the wall section of the cylinder head.
  • the sealing seat is arranged in such a way that it is arranged in a wall section running above the valve plate and above the inlet chamber and thus in particular the sealing seat simultaneously represents an opening for the inlet chamber opposite the valve plate.
  • the sealing seat simultaneously represents a mouth opening for the outlet chamber, so that a direct transition from the outlet chamber into the inlet chamber is realized through the sealing seat.
  • seal seat is arranged on a side of the inlet chamber opposite the valve plate.
  • a quick change of the closure piston between the closed position and the open position is preferably possible if, starting from the sealing seat, the stroke of the closure piston is in the range of a quarter to half of the average diameter of the connecting channel.
  • One solution provides that the mechanical power control unit is assigned to a cylinder and that, if necessary, several mechanical power control units are provided for several cylinders, whereby a mechanical power control unit does not necessarily have to be assigned to each cylinder.
  • a favorable solution provides that a cylinder head has an inlet chamber and an outlet chamber for a cylinder bank comprising at least two cylinders.
  • the respective mechanical power control unit is assigned to a bank of cylinders, in particular with at least two cylinders.
  • a mechanical power control unit is assigned to at least N-1 cylinder banks.
  • a mechanical performance control unit is assigned to each cylinder bank.
  • a check valve is provided in the compressor housing section following the refrigerant paths that can be influenced by the mechanical power control unit.
  • the check valve has an outlet opening provided in the valve plate and a valve element that interacts with the valve plate, so that the valve plate can also be used to arrange and form the check valve.
  • valve element is held on the valve plate, so that the valve plate is used not only to form the inlet and outlet valves, but also to hold the valve element of the check valve.
  • closure piston is acted upon by a compression spring in the direction of its position interacting with the sealing seat, so that the compression spring ensures that the closure piston closes the connecting channel due to the effect of the compression spring, for example when the refrigerant compressor is not working .
  • the closure piston can be actuated by a pressure chamber, which can be acted upon either by suction pressure or by high pressure, depending on the external control of the power control unit, with the closure piston moving into its open position when the pressure chamber is acted upon by suction pressure and when the pressure chamber is acted upon The locking piston is acted upon by high pressure in the direction of its closed position in addition to the action of the compression spring.
  • a volume of the pressure chamber is in particular so small that in the open position of the closure piston it is smaller than a third, preferably smaller than a quarter, even better smaller than a fifth, more advantageously smaller than a Sixth and particularly advantageously smaller than a seventh and even more advantageously smaller than an eighth of the maximum volume of the pressure chamber in the closed position of the closure piston.
  • This dimensioning of the pressure chamber allows it to be changed quickly between the closed position and the open position, since the pressure only has to be changed in a small volume between suction pressure and high pressure.
  • a control unit is preferably provided, which is included in the power control unit and can be used to control the pressurization of the closure piston.
  • a power control is preferably provided, which controls the at least one power control unit in accordance with a required compressor delivery capacity.
  • the performance control is in particular connected to a higher-level system control and receives information from the system control about the required compressor delivery capacity.
  • the power control then controls the at least one or more power control units so that the refrigerant compressor provides the required compressor delivery rate, but does not provide an unnecessarily high compressor delivery rate.
  • the refrigerant compressor is designed so that its maximum compressor delivery rate is sufficient for the maximum compressor delivery rate required by the system control, and lower compressor delivery rates are achieved by reducing power using the at least one performance control unit.
  • a start-up control unit is preferably provided for the refrigerant compressor, in particular the refrigerant compressor is provided with a start-up control unit which controls a start-up of the electric motor, which in the solution according to the invention starts as an asynchronous motor until it has reached the synchronous speed, and then as a synchronous motor continues.
  • the start-up control unit can control the operation of the refrigerant compressor in different ways in order to start the electric motor in a suitable manner.
  • the starting control unit works in such a way that it operates the electric motor for starting with a winding connection that reduces the starting current.
  • start-up control unit first energizes a first partial winding and then a second partial winding in a stator of the electric motor to start the electric motor.
  • Starting the electric motor with a first partial winding has the advantage that it makes it possible to reduce the starting current and thus, for example, avoid a heavy load on the electrical supply network due to an excessively high starting current.
  • the start-up control unit is designed such that it controls the power control when the electric motor starts up in such a way that the reciprocating compressor only works with a reduced compressor delivery capacity when the electric motor starts up.
  • start-up control controls the power control in such a way that the reciprocating compressor works with the smallest possible compressor delivery capacity when the electric motor starts up.
  • the smallest possible compressor delivery rate can be a compressor delivery rate at which one or more cylinders are still working.
  • a particularly favorable embodiment provides that the power of the reciprocating compressor can be controlled in such a way that, at the lowest possible compressor delivery rate, none of the cylinders compresses any more refrigerant, so that the torque required to start the reciprocating compressor is minimal.
  • an advantageous solution provides that the start-up control controls the power control in such a way that after synchronous operation of the electric motor has been achieved, the compressor delivery capacity is increased gradually, for example by switching on another cylinder or a further bank of cylinders or, if necessary, successively switching on additional cylinders or more Cylinder banks.
  • the reciprocating piston compressor according to the invention can work with all refrigerants common for semi-hermetic refrigerant compressors.
  • the solution according to the invention creates particular advantages for the operation of the reciprocating compressor, in particular for the damage-free operation of the reciprocating compressor when the reciprocating compressor operates with a suction pressure in the range of 10 bar to 50 bar.
  • the solution according to the invention is also particularly advantageous with regard to the mechanical load on the reciprocating compressor when the reciprocating compressor operates at a high pressure in the range of 40 bar to 160 bar.
  • the refrigerant compressor according to the invention can be used particularly advantageously if the reciprocating piston compressor works with carbon dioxide as the refrigerant and is designed in particular for operation with carbon dioxide as the refrigerant.
  • the task mentioned above is achieved according to the invention in a semi-hermetic refrigerant compressor of the type described above in that the electric motor is designed as a synchronous motor, in the rotor of which permanent magnets for the synchronous operation of the electric motor and a short-circuit cage for starting the electric motor in asynchronous operation are arranged.
  • the permanent magnets are designed as plate bodies, the flat sides of which extend in a longitudinal direction and a transverse direction running transversely to the longitudinal direction.
  • the permanent magnets are expediently arranged in the rotor in such a way that their longitudinal direction extends parallel to the rotor axis.
  • the permanent magnets are preferably arranged in the rotor in such a way that their transverse directions extend along outer edges of a geometric polygon that is symmetrical to the rotor axis.
  • the permanent magnets designed as plate bodies have a different magnetic polarity on their opposing flat sides, one of which faces the rotor axis and the other faces away from the rotor axis, so that flat magnetic poles are easily formed in the rotor are available for synchronous operation of the electric motor.
  • the electric motor can be cooled in a variety of ways.
  • suction-side refrigerant path passes through the motor housing to cool the electric motor.
  • An embodiment of a semi-hermetic refrigerant compressor according to the invention shown in Fig. 1 to 5 , comprises an overall housing 10, in which a reciprocating compressor 12 and an electric motor 14 are arranged.
  • the overall housing 10 preferably comprises a compressor housing section 22, which represents an outer housing of the reciprocating compressor 12, and a motor housing section 24, which represents an outer housing of the electric motor 14.
  • the overall housing 10 is preferably formed by a one-piece housing body 26, which extends in the direction parallel to a central axis 28 explained in detail below and is closed at the end on the side of the compressor housing section 22 by means of a bearing cover 32 and in the area of the motor section 24 at the end with an end cover 34 is closed.
  • a compressor shaft designated as a whole by 42 extends coaxially to the central axis 28 between a first shaft bearing 44 arranged on the bearing cover 32 to a second shaft bearing 46 arranged between the reciprocating compressor 12 and the electric motor 14, the second shaft bearing 46 being on an in
  • the middle wall 48 is held in the housing body 26, which has a between the bearing cover 32 and the middle wall 48 drive space 52, through which the compressor shaft 42 extends and in which eccentrics 54 and 56 of the compressor shaft 42 are arranged, with two connecting rods 62 1 and 62 2 on each of the eccentrics 54 and 56, or 64 1 and 64 2 , are arranged, with the connecting rods 62 1 and 64 1 driving the pistons 66 1 and 68 1 and the connecting rods 62 2 and 64 2 driving the pistons 66 2 and 68 2 .
  • the pistons 66 and 68 are guided in cylinder bores 72 and 74, which are formed by cylinder housings 76, 78 which are formed into the compressor housing section 22, in particular in one piece.
  • the two first cylinders 82 1 and 84 1 molded into the compressor housing section 22 form a first cylinder bank 86 1
  • the two cylinders 82 2 and 84 2 molded into the compressor housing section 22 form a second cylinder bank 86 2 .
  • each of the cylinder banks 86 1 and 86 2 the respective cylinder bores 72 1 and 74 1 or 72 2 and 74 2 are closed by a common valve plate 88 1 or 88 2 , which seals tightly on the respective cylinder housings 76 1 and 78 1 , or 76 2 and 78 2 , and thus limit the compression space enclosed by the respective valve plate 88 1 and 88 2 and the respective pistons 66 1 and 68 1 or 66 2 and 68 2 as well as the cylinder bores 72 1 and 74 1 or 72 2 and 74 2 .
  • valve plates 88 1 and 88 2 are in turn covered by cylinder heads 92 1 and 92 2 , respectively.
  • each of the cylinder heads 92 1 and 92 2 is as in the Fig. 6 to 8 shown, an inlet chamber 94 and an outlet chamber 96 are arranged, which are assigned to the two cylinders 82 and 84 of the respective cylinder bank 86.
  • the inlet chamber 94 lies over inlet openings 102 and 104 of the cylinder 82 and inlet openings 106 and 108 of the cylinder 84.
  • outlet chamber 96 lies above outlet openings 112 and 114 of the cylinder 82 arranged in the valve plate 88 and outlet openings 116 and 118 of the cylinder 84, which are provided with outlet valves 113, 115, 117, 119 seated on the valve plate 88, and in particular is directly adjacent these on.
  • each cylinder head 92 comprises an outer body 122, which engages over the respective valve plate 88 and encloses the inlet chamber 94 and the outlet chamber 96, which in turn are separated from one another by a separating body 124 running within the outer body 122, the separating body 124 extending from the respective valve plate 88 rises and extends over and across the inlet chamber 94.
  • the outlet chamber 96 lies laterally next to the inlet chamber 94 in the area of the valve plate 88 and, however, extends between the outer body 122 and the separating body 124 at least in some areas above the inlet chamber 94.
  • each cylinder head 92 is assigned a mechanical power control unit 142, which is actively controlled by a power control 138 and with which a connecting channel 144 between the outlet chamber 96 and the inlet chamber 94 is closed or opened can be, with the cylinders 82, 84 assigned to the cylinder head 92 with the connecting channel 144 ( Fig. 7 ) compress refrigerant at full power and do not compress refrigerant when the connecting channel 144 is open, since the refrigerant flows back from the outlet chamber 96 into the inlet chamber 94.
  • the connecting channel 144 runs through an insert part 146 inserted into the separating body 124, which forms a sealing seat 148 which faces the outlet chamber 96 and which adjoins a part of the outlet chamber 96 surrounding the sealing seat 148 and adjoining it.
  • the sealing seat 148 faces a closure piston 152, which can be placed on the sealing seat 148, for example with a metallic sealing area 154, in order to seal the connecting channel 144 tightly and which can be lifted off so far from the sealing seat 148 that the sealing area 154 is at a distance from the seal seat 148 and thus refrigerant can flow from the outlet chamber 96 into the inlet chamber 94.
  • the closure piston 152 is guided coaxially to the insert part 146 with the seal seat 148 and sealed by means of a piston ring 153 in a guide bore 156, which is formed by a guide sleeve body 158 of the cylinder head 92 which is molded onto the outer body 122.
  • the closure piston 152 itself or at least the sealing area 154 is made of a metal, for example a non-ferrous metal, which has a lower hardness than the metal of the seal seat 148, which is made for example of steel, in particular hardened steel.
  • a stroke of the closure piston 152 between a closed position and an open position is in the range between a quarter and half of an average diameter of the connecting channel 144.
  • the closure piston 152 delimits a pressure chamber 162, which is arranged on a side of the closure piston 152 facing away from the sealing area 154 and is closed by a closing body 164 on a side opposite the closure piston 152.
  • the volume of the pressure chamber 162 is in particular so small that in the open position of the closure piston it is smaller than a third, better smaller than a quarter, even better smaller than a fifth, advantageously smaller than a sixth and even more advantageously smaller than an eighth of the maximum Volume of the pressure chamber 162 in the closed position of the closure piston 152.
  • a compression spring 166 is arranged in the pressure chamber 162, which is supported on the end body 164 on the one hand and, on the other hand, acts on the closing piston 152 in the direction of its closed position resting on the sealing seat 148.
  • the closing piston 152 is in its in Fig. 8 shown open position or in its in Fig. 7 shown locking position movable.
  • the closure piston 152 is penetrated by a throttle channel 172, which extends from the pressure chamber 162 through the closure piston 152 to a mouth opening which is arranged radially outside of the sealing area 154 on a side facing the sealing seat 148, but in that this is radially outside the sealing element 154 lies, in the closed position of the closure piston 152 an entry of refrigerant under pressure in the outlet chamber 96 and flowing around the seal seat is permitted and this is throttled to the pressure chamber 162.
  • a throttle channel 172 which extends from the pressure chamber 162 through the closure piston 152 to a mouth opening which is arranged radially outside of the sealing area 154 on a side facing the sealing seat 148, but in that this is radially outside the sealing element 154 lies, in the closed position of the closure piston 152 an entry of refrigerant under pressure in the outlet chamber 96 and flowing around the seal seat is permitted and this is throttled to the pressure chamber 162.
  • a relief channel 176 leads into the pressure chamber 162, for example through the closure body 164, which can be connected to a pressure relief channel 184, which is connected to the inlet chamber 94, through a solenoid valve designated as a whole by 182.
  • the solenoid valve 182 is designed such that it has a valve body 186 with which the connection between the pressure relief channel 184 and the relief channel 176 can be interrupted or established.
  • the suction pressure predominates in the pressure chamber 162, while the closure piston 152 is acted upon by the pressure in the outlet chamber 96 on its side facing the outlet chamber 96 and is thus moved into its open position.
  • the compression spring 166 presses the closure piston 152 onto the sealing seat 148 and additionally high pressure flows through the throttle channel 172 into the pressure chamber 162, so that in the pressure chamber 162 High pressure builds up, which, in addition to the effect of the compression spring 166, presses the closure piston 152 with the sealing element 154 onto the seal seat 148.
  • the closing piston 152 is designed such that it extends radially beyond the sealing seat 148, so that even when the closing piston 152 is in the closed position, the piston surface lying radially outside the sealing seat 148 and subjected to high pressure This causes the closing piston 152 to move into the open position against the force of the compression spring 166, shown in Fig. 5 is moved if the valve body 186 of the solenoid valve 182 establishes the connection between the relief channel 176 and the pressure relief channel 184, which results in a suction pressure being established in the pressure chamber 162.
  • the supply of refrigerant under suction pressure takes place via a supply channel 202 formed in the compressor housing section 22, which leads to an inlet opening 204 leading to the valve plate 88, through which refrigerant under suction pressure flows to a passage opening 206 in the valve plate 88 and through this into the inlet chamber 94 passes.
  • outlet chamber 96 to an outlet opening 212 arranged in the valve plate 88 through which the refrigerant under pressure in the outlet chamber 96 passes into an outlet channel 214 provided in the compressor housing section 22 and can flow to an outlet connection element 216.
  • the outlet opening 212 of the valve plate 88 is assigned a check valve 222, which is held on the valve plate 88 and a valve element 224 is arranged on a side of the valve plate 88 facing the outlet channel 214 and ensures that in the case of the open position of the closing piston 152 and thus In the event of the refrigerant overflowing from the outlet chamber 96 into the inlet chamber 94, the pressure in the outlet channel 214 does not drop, but is maintained by the closing check valve 222.
  • the check valve 222 together with a catch element 226 assigned to it, is held on the valve plate 88 by means of a holding element 228 and seals against the valve plate 88.
  • the refrigerant compressor according to the invention is designed as a semi-hermetic compressor, so that refrigerant under suction pressure is supplied to an engine compartment 234 by means of an inlet connection element 232 arranged on the end cover 34 and flows through the electric motor 14 in the direction of the middle wall 48 and passes from the engine compartment 234 into the supply channel 202, so that the supplied suction-side refrigerant cools the electric motor 14 in the engine compartment 234.
  • the electric motor 14 in turn comprises a stator 252 which is held firmly in the motor housing section 24 and has a stator winding 254, which has, for example, two partial windings 256 and 258 which are used to magnetize a stator laminated core 262.
  • the stator 252 encloses a rotor designated as a whole 272, in the rotor laminated core 274, as in Fig. 9 shown, on the one hand a short-circuit cage 276 is arranged, which comprises short-circuit bars 278 which run parallel to a rotor axis 282 and which are electrically conductively connected to one another at the ends in the circumferential direction.
  • plate-shaped permanent magnets 292 are inserted into the laminated core 274, the flat sides 294 of which extend on the one hand with a longitudinal direction 296 parallel to the rotor axis 282 and with a transverse direction 298 extend transversely to the rotor axis 282 in such a way that the transverse directions 298 extend around the rotor axis 282 as an axis of symmetry form a geometric polygon running around it.
  • the permanent magnets 292 are further designed such that in a direction of rotation 302 around the rotor axis 282, successive permanent magnets 292 each have an alternating polarity on their sides facing the rotor axis 282, so that overall the rotor 272 has alternating magnetic poles in the direction of rotation by means of the permanent magnets 292 .
  • An electric motor 14 provided with such a rotor 272 works as a synchronous motor in normal operation due to the permanent magnets 292 provided in the rotor 272, with such a synchronous motor having advantageous energy efficiency and higher refrigerant delivery capacity due to the permanent magnets 292.
  • the rotating field generated by the stator 252 rotates at a defined frequency due to a supply to the stator winding 254, which is caused, for example, by the fact that the stator winding 254 is fed by an AC network.
  • the rotor 272 is provided with the short-circuit cage 276, which creates the possibility that the electric motor 14 initially starts as an asynchronous motor until it reaches the speed corresponding to the rotating field of the stator winding has reached and then rotates as a synchronous motor due to the magnetic poles caused by the permanent magnets 292.
  • a refrigerant compressor with such an electric motor can therefore be operated powered by a standard AC network, since it starts like an asynchronous motor.
  • the start-up control 312 intervenes in the intended power control 138 for the active control of the power control units 142 and causes at least one cylinder bank 86, preferably both cylinder banks 86 1 and 86 2 , can be deactivated, so that when at least one cylinder bank 86 is deactivated, the torque that the reciprocating compressor 12 requires is reduced, and when both cylinder banks 86 1 and 86 2 are deactivated, the torque that the reciprocating compressor 12 requires is low, since none Compression of refrigerant takes place so that, on the one hand, the starting current of the electric motor 14 is kept low and, on the other hand, it then changes very quickly from its operation as an asynchronous motor to operation as a synchronous motor in which the full torque is available, so that the cylinder banks either simultaneously or successively 86 1 and 86 2 can be activated ( Fig. 10 ).
  • the catching element 226 'of the check valve 222' is formed in the compressor housing section 22, for example by a recess on the side of the outlet channel 214, which limits the possible path of the valve element 224' between its closed position resting on the valve plate 88 and the maximum open position Position limited.
  • Such a catching element 226 ' can generally be provided in all compressor housing sections 22 of all refrigerant compressors of the same assembly, regardless of whether they are provided with a check valve 222' or not, so that the refrigerant compressor can be easily retrofitted with a check valve 222' and in particular also with at least a mechanical power control unit 142 according to the invention together with such a check valve 222 'is possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP23195632.7A 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique Pending EP4276311A3 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP23195632.7A EP4276311A3 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP23195632.7A EP4276311A3 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique
EP16778057.6A EP3523537B1 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique
PCT/EP2016/074063 WO2018065071A1 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP16778057.6A Division EP3523537B1 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique
EP16778057.6A Division-Into EP3523537B1 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique

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Publication Number Publication Date
EP4276311A2 true EP4276311A2 (fr) 2023-11-15
EP4276311A3 EP4276311A3 (fr) 2024-01-10

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EP23195632.7A Pending EP4276311A3 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique
EP16778057.6A Active EP3523537B1 (fr) 2016-10-07 2016-10-07 Compresseur frigorifique semi-hermétique

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Country Status (6)

Country Link
US (1) US20190234392A1 (fr)
EP (2) EP4276311A3 (fr)
CN (2) CN109715945B (fr)
AU (1) AU2016425930B2 (fr)
RU (1) RU2745598C2 (fr)
WO (1) WO2018065071A1 (fr)

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* Cited by examiner, † Cited by third party
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US11635091B2 (en) 2020-03-13 2023-04-25 Honeywell International Inc. Compressor with integrated accumulator
EP4279739A1 (fr) * 2022-05-17 2023-11-22 Valeo Klimasysteme GmbH Dispositif de sortie d'un compresseur

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Also Published As

Publication number Publication date
CN113294311B (zh) 2023-08-29
BR112019006964A2 (pt) 2019-07-02
EP4276311A3 (fr) 2024-01-10
RU2019112862A (ru) 2020-11-09
RU2745598C2 (ru) 2021-03-29
AU2016425930B2 (en) 2021-03-25
RU2019112862A3 (fr) 2020-11-09
WO2018065071A1 (fr) 2018-04-12
EP3523537A1 (fr) 2019-08-14
US20190234392A1 (en) 2019-08-01
CN109715945B (zh) 2021-07-23
AU2016425930A1 (en) 2019-04-18
CN113294311A (zh) 2021-08-24
EP3523537B1 (fr) 2024-05-01
CN109715945A (zh) 2019-05-03

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