EP1014016A2 - Systèmes de conditionnement d'air - Google Patents
Systèmes de conditionnement d'air Download PDFInfo
- Publication number
- EP1014016A2 EP1014016A2 EP99125415A EP99125415A EP1014016A2 EP 1014016 A2 EP1014016 A2 EP 1014016A2 EP 99125415 A EP99125415 A EP 99125415A EP 99125415 A EP99125415 A EP 99125415A EP 1014016 A2 EP1014016 A2 EP 1014016A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- passage
- driving chamber
- valve
- compressor
- pressure
- 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.)
- Withdrawn
Links
Images
Classifications
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
-
- 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
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/184—Valve controlling parameter
- F04B2027/1854—External parameters
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
- F04B2027/1868—Crankcase pressure
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
Definitions
- the present invention relates to air conditioning systems that utilize refrigerants and a compressor, and particularly to air conditioning systems capable of effectively alleviating excessive increases in refrigerant discharge pressure within a heating circuit.
- a known air conditioning system is disclosed in Japanese Unexamined Patent Publication No. 7-19630 and includes a compressor 1, a cooling circuit 51, a heating circuit 52 and a controller 83, as shown in FIG. 1.
- the cooling circuit 51 includes a condenser 55, a first expansion valve 57, and a heat exchanger 59 provided on a passage connecting a discharge port D to a suction port S of the compressor 1. High-pressure refrigerant discharged from the discharge port of the compressor 1 is drawn through the above respective devices and back to the compressor 1.
- the heating circuit 52 includes a bypass passage 52a that extends from the discharge port D of the compressor 1 to the heat exchanger 59.
- a second expansion valve 63 is provided within the bypass passage 52a between the discharge port D and the heat exchanger 59.
- the high pressure refrigerant discharged from the compressor 1 is not directed to the condenser 55, but rather is drawn by the compressor 1 through the second expansion valve 63 and the heat exchanger 59 and this cycle is repeated.
- Such a heating circuit 52 is generally known as a hot-gas bypass heater.
- the operation of the cooling circuit 51 and the heating circuit 52 is changeably selected by opening and closing selector valves 53a and 53b, which opening and closing operations are performed by the controller 83.
- the air conditioning system is used in a state in which the refrigerant discharge pressure is higher when the heating circuit 52 is used than when the cooling circuit 51 is used, abnormally high pressure is likely to be applied during operation of the heating circuit 52.
- the abnormally high-pressure state is likely to occur when a rotation speed of the compressor 1 is increased temporarily during operation of the heating circuit 52. Therefore, the air conditioning system is further provided with a refrigerant releasing passage 91 having a pressure relief valve 93.
- the refrigerant releasing passage 91 is connected to the heating circuit 52 and the cooling circuit 51 and the pressure relief valve 93 can be opened to release the refrigerant from the heating circuit 52 to the cooling circuit 51 when the refrigerant discharge pressure abnormally increases during the operation of the heating circuit 52.
- the refrigerant is released toward the cooling circuit 51 which is not used when the discharge pressure is increased abnormally during operation of the heating circuit 52, thereby preventing the discharge pressure at the heating circuit 52 from increasing abnormally.
- the refrigerant is released from the operating heating circuit 52 to the cooling circuit 51 which is not used, the abnormally high-pressure state of the discharge pressure during operation of the heating circuit 52 can be alleviated.
- the refrigerant in the heating circuit 52 is released into the cooling circuit 51 whenever the discharge pressure increases, the amount of the refrigerant in the heating circuit 52 is reduced and heating performance may be reduced.
- the high- pressure refrigerant is wastefully released from the heating circuit by working the compressor 1, energy efficiency is reduced.
- an object of the present invention to provide an air conditioning system that can effectively alleviate abnormally high-pressure state.
- An air conditioning system may preferably include a compressor, a heating circuit, and a compressor output discharge capacity controller.
- the compressor may have a suction port for drawing refrigerant, a discharge port for discharging compressed refrigerant, a driving unit provided within the compressor driving chamber, a first passage that connects the discharge port to the driving chamber, and a second passage that connects the driving chamber to the suction port.
- the driving unit may decrease compressor output discharge capacity when pressure within the driving chamber increases.
- the heating circuit may have a passage that extends from the discharge port to the suction port through a heat exchanger.
- the capacity controller may open the first passage when the refrigerant discharge pressure results predetermined pressure state and the capacity controller may narrow the second passage in response to the opening of the first passage.
- the capacity controller may narrow the second passage in response to the opening of the first passage.
- an air conditioning system may include a compressor, a heating circuit, and a compressor output discharge capacity controller.
- the compressor may have a suction port, a discharge port, a driving unit, a first passage and a second passage.
- the suction port may draw the refrigerant into the compressor.
- the discharge port may discharge compressed high-pressure refrigerant.
- the driving unit may be provided within a compressor driving chamber. The driving unit may decrease compressor output discharge capacity when the pressure within the driving chamber increases.
- the first passage may connect the discharge port to the driving chamber.
- the second passage may connect the driving chamber to the suction port.
- the heating circuit may have a passage that extends from the discharge port to the suction port through the heat exchanger.
- Such type of the heating circuit is generally known as a hot gas bypass heater.
- a decompressor such as an expansion valve may be provided within the passage from the discharge port to the heat exchanger.
- the capacity controller may close the first passage when the refrigerant discharge pressure does not result predetermined pressure state. By closing the first passage, the high-pressure refrigerant can not be released from the discharge port to the driving chamber, the pressure within the driving chamber does not increase and the compressor output discharge capacity can not be decreased thereby maintaining high circuit operation performance. To the contrary, the capacity controller may open the first passage when the refrigerant discharge pressure results predetermined pressure. By opening the first passage, the high pressure refrigerant may be released from the discharge port to the driving chamber through the first passage. Further, the capacity controller may narrow the second passage in response to the opening of the first passage.
- pressure within the driving chamber can be quickly increased and the necessary amount of refrigerant to be released from the discharge port into the driving chamber can be reduced, because high-pressure refrigerant released from the discharge port into the driving chamber is difficult to be released into the suction port through the narrowed second passage.
- pressure within the driving chamber can be quickly increased to decrease the compressor output discharge capacity quickly. Therefore, even if the refrigerant discharge pressure increases sharply, the alleviation of the abnormally high discharge pressure can be started at an early stage of such increase of the discharge pressure.
- the high-pressure state within the driving chamber can be maintained relatively for long time, because the second passage narrowed by the capacity controller prevents the refrigerant within the driving chamber from being released quickly into the suction port.
- the second passage may preferably be narrowed by throttling the second passage.
- the second passage may be closed, instead of being narrowed, in response to the opening of the first passage.
- the refrigerant released from the discharge port into the driving chamber can be fully retained within the driving chamber. Therefore, the necessary time and the necessary amount of refrigerant for increasing the pressure within the driving chamber can be minimized.
- the capacity controller may preferably have a first valve disposed within the first passage and a second valve disposed within the second passage.
- the first valve may open the first passage when the refrigerant discharge pressure results predetermined pressure state.
- the second valve may narrow or close the second passage in response to the opening of the first valve.
- the first valve and the second valve are one of the features that corresponds to the capacity controller or the capacity control means.
- driving chamber decompression means may preferably be provided in the air conditioning system.
- the driving chamber tends to be brought into an abnormally high pressure state because the second passage is narrowed or closed in order to increase the pressure within the driving chamber for decreasing the compressor output discharge capacity. If the pressure within the driving chamber exceeds the upper tolerance level of the driving chamber, the airtight seal of the driving chamber will be degraded. Therefore, the driving chamber decompression means may release the refrigerant from the driving chamber into the suction port separately from the second passage when the pressure within the driving chamber results predetermined high-pressure state.
- the driving chamber decompression means may preferably have a driving chamber decompression passage that connects the driving chamber to the suction port separately from the second passage and a driving chamber decompression valve that is provided within the driving chamber decompression passage.
- the driving chamber decompression valve opens the driving chamber decompression passage thereby releasing the high-pressure refrigerant from the driving chamber into the suction port in order to decrease the pressure within the driving chamber.
- the driving chamber decompression valve may open the driving chamber decompression passage based on the difference between the pressure within the driving chamber and lower pressure than the pressure within the driving chamber. For example, compressor suction pressure, atmospheric pressure or vacuum pressure may be utilized. Otherwise, the driving chamber decompression valve may open the driving chamber decompression passage by utilizing a valve-opening signals generated on the basis of the pressure within the driving chamber.
- the capacity controller may close the first passage and open the second passage. By closing the first passage, the refrigerant can not be released from the discharge port to the driving chamber. By opening the second passage, the high-pressure refrigerant within the driving chamber is released into the suction port.
- the refrigerant released from the driving chamber into the suction port through the second passage is drawn by the suction port and again compressed and discharged.
- a representative air conditioning system 100 may include a cooling circuit 151, a heating circuit 152 and a variable displacement compressor 101 as a driving source for both the heating and cooling circuits.
- a representative capacity controller is shown in FIG. 3, but is not shown in FIG. 2 for the sake of convenience and will be described below in further detail.
- Such the air conditioning system 100 may be utilized in a vehicle-mounted air conditioning system.
- a driving shaft 125 of the compressor 100 may be coupled to and driven by an automobile engine 170.
- the cooling circuit 151 may be driven by high-pressure refrigerant, which is compressed by the compressor 101, and may include a condenser 155, a first expansion valve 157, a heat exchanger 159 and an accumulator 161. These devices may be disposed within a path 151a that extends from a discharge port D to a suction port S of the compressor 101.
- the heat exchanger 159 is also generally known as an evaporator.
- the heat exchanger 159 may be arranged side by side with a hot-water heater 171, which circulates hot coolant from the engine 170 through a pipe 173.
- the heating circuit 152 is driven by high-temperature and high-pressure refrigerant, which is also compressed by the compressor 101, and may include a second expansion valve 163, the heat exchanger 159 and the accumulator 161. These devices may be disposed on a bypass passage 152a for introducing the refrigerant discharged from the discharge port D to the heat exchanger 159. In other words, the heating circuit 152 partially overlaps with the cooling circuit 151.
- Such a heating circuit 152 is also generally known as a hot-gas bypass heater.
- a first open/close valve 153a and a second open/close valve 153b may be utilized as switch valves for alternatively actuating the cooling circuit 151 and the heating circuit 152.
- the refrigerant is compressed by the compressor 101 to attain a high temperature and high pressure state.
- the compressed refrigerant is sent to the condenser 155, where heat from the high-temperature refrigerant is dissipated to the outside environment and the refrigerant is liquefied.
- the refrigerant is decompressed by the first expansion valve 157 and sent to the heat exchanger 159 where the refrigerant absorbs outside heat and is gasified.
- the gasified refrigerant is returned to the compressor 101 again through the accumulator 161 for re-circulation throughout the system 100.
- the refrigerant is compressed by the compressor 101 to attain a high temperature and high pressure state.
- the compressed refrigerant is then decompressed by the second expansion valve 163 and sent to the heat exchanger 159, where beat from the compressed refrigerant is dissipated to the outside environment.
- the refrigerant is constantly in a gaseous state while circulating through the heating circuit 152.
- the heating circuit 152 may be used as an auxiliary heater. Heat generated by the heat exchanger 159 during operation of the heating circuit 152 may be used as an auxiliary heating source for the hot water heater 171. The heating circuit 152 also may be used to assist the coolant from the engine 170 when the coolant can not provide sufficient heat to start the engine 170 in a low-temperature environment, such as an outside air temperature of - 20 °C or so.
- a representative compressor 101 may include a driving chamber 110 defined within a housing 101a of the compressor 101 and a swash plate 130 that is rotatably supported by the driving shaft 125 in the driving chamber 110.
- the swash plate 130 may be supported by the driving shaft 125 and may rotate together with the driving shaft 125.
- the swash plate 130 is inclined with respect to the driving shaft 125 when the driving shaft 125 rotates and the inclination angle of the swash plate 130 with respect to a plane perpendicular to the axis of rotation of the driving shaft 125 is changeable.
- the peripheral edge portion of the swash plate 130 may be connected to the head portions of the pistons 135 by means of movable shoes 131.
- Six pistons 135 in total may be disposed around the driving shaft 125 (however, only one piston is shown in FIG. 3 for the sake of convenience) and may be laterally slide within six cylinder bores 109. The circumferential positions of the six cylinder bores 109 are fixed by the compressor housing 101a.
- a suction port 118a and a discharge port 123a are defined in a bottom portion of each the cylinder bore 109.
- a suction valve 118 is positioned to correspond to the suction port 118a and a discharge valve 123 is positioned to correspond to the discharge port 123a.
- Each suction port 118a communicates with a suction chamber 115 and each the discharge port 123a communicates with a discharge chamber 120.
- the output discharge capacity of the compressor 101 is determined by the stroke length of the piston 135, which is determined by the degree of change in inclination angle of the swash plate 130 during each cycle. That is, the further the swash plate 130 is withdrawn from the cylinder bore 109 during each cycle, the longer the stroke length of the piston 135 will be. As the stroke length decreases, the output discharge capacity of the compressor 101 also decreases.
- the inclination angle of the swash plate 130 is determined, in part, by the difference in pressure on the opposite sides of the piston 135, i.e., the pressure difference between driving chamber pressure and the cylinder bore pressure. Increasing or decreasing the driving chamber pressure can adjust this pressure difference.
- the pressure within the driving chamber 110 is increased, the swash plate 130 does not move as much in the lateral direction and the stroke length of the piston 135 decreases. Therefore, the output discharge capacity also will decrease.
- the output discharge capacity decreases, the refrigerant discharge pressure decreases and the suction pressure increases.
- the pressure within the driving chamber 110 is decreased, the swash plate 130 will move further in the lateral direction, the stroke length of the piston 135 increases. In this case, the output discharge capacity will increase.
- the refrigerant discharge pressure increases and the suction pressure decreases.
- the high-pressure refrigerant in the discharge chamber 120 is released into the driving chamber 110 to increase the pressure within the driving chamber 110.
- the refrigerant in the discharge chamber 120 is prevented from being released into the driving chamber 110.
- the discharge chamber 120 is connected to the driving chamber 110 by a heating circuit capacity control passage 201 and also by a cooling circuit capacity control passage 301.
- a heating circuit capacity control valve 181 is provided within the heating circuit capacity control passage 201.
- the heating circuit capacity control valve 181 includes a valve body 211 provided between a first capacity control chamber 221 and a second capacity control chamber 223.
- the first capacity control chamber 221 and the second capacity control chamber 223 can communicate with each other through a connecting passage 225 when the valve body 211 opens the connecting passage 225.
- the valve body is biased by a spring 211a such that the valve body 211 closes the connecting passage 225.
- the discharge chamber 120 is connected with the first capacity control chamber 221 by a first heating circuit capacity control passage 203. Therefore, pressure in the first heating circuit capacity control passage 203 and the pressure in the first capacity control chamber 221 are equal to the discharge pressure Pd.
- the driving chamber 110 is connected with the second capacity control chamber 223 by a second heating circuit capacity control passage 205. Therefore, pressure in the second heating circuit capacity control passage 205 and the pressure in the second capacity control chamber 223 are equal to the pressure Pc within the driving chamber 110.
- the driving chamber 110 is connected to the suction chamber 115 by a refrigerant bleeding passage 202.
- a refrigerant bleeding valve 185 is provided onto the refrigerant bleeding passage 202.
- the refrigerant bleeding valve 185 includes a valve body 213 provided between a first refrigerant bleeding chamber 231 and a second refrigerant bleeding chamber 233.
- the valve body 213 is biased by a spring 213a.
- the first refrigerant bleeding chamber 231 and the second refrigerant bleeding chamber 233 are communicated with each other through a connecting passage 235 during a normal operation of the heating circuit.
- the first refrigerant bleeding chamber 231 is connected with the driving chamber 110 by a first refrigerant bleeding passage 207.
- pressure in the first refrigerant bleeding passage 207 and the first refrigerant bleeding chamber 231 are equal to the pressure Pc within the driving chamber 110.
- the second refrigerant bleeding chamber 233 is connected with the suction chamber 115 by a second refrigerant bleeding passage 209. Therefore, pressure in the second refrigerant bleeding passage 209 and the second refrigerant bleeding chamber 233 are equal to the suction pressure Ps.
- the heating circuit capacity control valve 181 and the refrigerant bleeding valve 185 are integrally provided within the compressor housing 101a.
- the valve body 213 for opening /closing the refrigerant bleeding passage 202 is coupled to the valve body 211 for opening/closing the heating circuit capacity control passage 201 by a connecting member 215.
- the valve body 211 of the heating circuit capacity control valve 181 is located to close the heating circuit capacity control passage 201
- the valve body 213 of the refrigerant bleeding valve 185 is located to narrow the refrigerant bleeding passage 202.
- locations of both valve bodies 211, 213 are adjusted by controlling the biasing force of the springs 211a and 213a or by disposing a spacer between the valve body 213 and the connecting passage 235 such that the valve body 213 is spaced with respect to the connecting passage 235 even when the valve body 213 is to move towards the connecting passage 235.
- the discharge chamber 120 is connected to the driving chamber 110 by the cooling circuit capacity control passage 301 as well as the heating circuit capacity control passage 201.
- a cooling circuit capacity control valve 183 is provided within the cooling circuit capacity control passage 301.
- the discharge chamber 120 is connected with the cooling circuit capacity control valve 183 by a first cooling circuit capacity control passage 301a. Therefore, pressure in the first cooling circuit capacity control passage 301a is equal to the discharge pressure Pd.
- the cooling circuit capacity control valve 183 is connected with the driving chamber 110 by a second cooling circuit capacity control passage 301b. Therefore, pressure in the second cooling circuit capacity control passage 301b is equal to the pressure Pc in the driving chamber 110.
- the cooling circuit capacity control valve 183 includes a valve body 305, an actuating member 307a actuated by a solenoid 307, a connecting member 307b for connecting the actuating member 307a to the valve body 305 and a bellows 305a.
- the bellows 305a can expand and contract to move the valve body 305 in accordance with the suction pressure Ps.
- the suction pressure Ps for expanding or contracting the bellows 305a may be detected through a suction pressure detecting passage 303 that is connected to the suction chamber 115.
- the bellows 305a opens the valve body 305 to communicate the first cooling circuit capacity control passage 301a with the second cooling circuit capacity control passage 301b when the suction pressure Ps satisfies the condition of opening the valve body 305.
- Such condition may be changed by exciting or not exciting the solenoid 307.
- a controller (not particularly shown in the drawings) generates a control signal for exciting the solenoid 307. This is because the force exerted onto the actuating member 307a by the solenoid 307 is utilized as a biasing force against the movement of the bellows 305a.
- the solenoid 307 is excited to close the cooling circuit capacity control valve 183, because the output discharge capacity is to be controlled exclusively by utilizing the heating circuit capacity control valve 181 during operation of the heating circuit.
- the valve body 213 of the refrigerant bleeding valve 185 is moved downward in FIG.3 in response to the downward movement of the valve body 211 of the capacity control valve 181.
- the refrigerant bleeding passage 202 is narrowed by the refrigerant bleeding valve 185 in response to the opening of the capacity control valve 181.
- the discharge chamber 120 is communicated with the driving chamber 110 through the heating circuit capacity control passage 201.
- the high-pressure refrigerant is released from the discharge chamber 120 into the driving chamber 110.
- the refrigerant released into the driving chamber 110 is difficult to be released into the suction chamber 115 because the refrigerant bleeding passage 202 is narrowed.
- the pressure within the driving chamber 110 is quickly increased and the high pressure state in the driving chamber 110 is maintained relatively for long time.
- the swash plate 130 stands to decrease the stroke length of the pistons 135, the compressor output discharge capacity is decreased and the compressor discharge pressure is decreased thereby alleviating the abnormally high discharge pressure quickly.
- the necessary amount of the refrigerant for increasing the pressure within the driving chamber 110 can be reduced, because the refrigerant bleeding passage 202 is narrowed in response to the opening of the capacity control passage 201 and therefore, the pressure within the driving chamber 110 can be quickly and sufficiently increased by releasing only small amount of the high-pressure refrigerant into the driving chamber 110. Therefore, extreme reduction of the energy efficiency does not occur.
- the difference between the discharge pressure Pd and the pressure Pc within the driving chamber 110 does not increase. Therefore, pressure within the first capacity control chamber 221 (equal to the discharge pressure) does not prevail over the biasing force of the springs 211a, 213a and the pressure within the second capacity control chamber 223.
- the valve body 211 does not move to open the heating circuit capacity control passage 201 and the refrigerant bleeding valve 185 does not narrow the refrigerant bleeding passage 202.
- the capacity control passage 201 is not opened and the refrigerant bleeding passage 202 is not narrowed.
- the high-pressure refrigerant can not be released from the discharge chamber 120 into the driving chamber.
- the pressure within the driving chamber 110 is not increased, the compressor output discharge capacity is not decreased and the compressor discharge pressure is not decreased thereby maintaining the high operating performance of the heating circuit.
- the cooling circuit capacity control valve 183 is closed. As the result, the discharge chamber 120 does not communicate with the driving chamber 110. The high-pressure refrigerant is not released from the discharge chamber 120 into the driving chamber 110. Thus, the pressure within the driving chamber 110 does not increase, the inclination angle of the swash plate 130 does not increase, the output discharge capacity does not decrease, thereby maintaining high cooling performance.
- the bellows 305a of the cooling circuit capacity control valve 183 moves the valve 305 to communicate the first cooling circuit capacity control passage 301a with the second cooling circuit capacity control passage 301b.
- the high-pressure refrigerant is released from the discharge chamber 120 into the driving chamber 110 through the cooling circuit capacity control passage 301.
- the pressure within the driving chamber 110 increases and the compressor output discharge capacity decreases.
- the suction pressure Ps increases and the heat exchanger 159 (shown in FIG.2) is prevented from being frosted.
- the cooling circuit capacity control valve 183 is necessarily to be closed because the discharge pressure is to be controlled exclusively by the heating circuit capacity control valve 181. Therefore, when the heating circuit is operated, the solenoid 307 in the cooling circuit capacity control valve 183 is not excited. Thus, the cooling circuit capacity control passage 301 is closed during the operation of the heating circuit.
- the heating circuit capacity control valve 181 is necessarily to be closed because the suction pressure is to be controlled exclusively by utilizing the cooling circuit capacity control valve 183.
- the heating circuit capacity control valve 181 utilizes the difference between the discharge pressure Pd and the pressure within the driving chamber 110. Therefore, during operation of the cooling circuit, the heating circuit capacity control valve 181 may possibly be opened when the discharge pressure Pd particularly increases with respect to the pressure within the driving chamber 110.
- the pressure necessary for opening the heating circuit capacity control valve 181 is set to be higher than the discharge pressure utilized during the operation of the cooling circuit. Therefore, the heating circuit capacity control valve 181 is unlikely opened during operation of the cooling circuit.
- the heating circuit capacity control valve 181 is swiftly closed causing no practical damage onto the air conditioning system.
- the refrigerant bleeding valve 185 narrows the refrigerant bleeding passage 202 in response to the opening of the capacity control valve 181.
- the refrigerant in the driving chamber 110 is difficult to be released into the suction chamber 115 and the pressure within the driving chamber 110 can be quickly increased for alleviating the abnormally high discharge pressure.
- each spring 211a, 213a may preferably be adjusted such that the valve body 213 of the refrigerant bleeding valve 185 closes the refrigerant bleeding passage 202 when the valve body 212 in the capacity control valve 181 opens the heating circuit capacity control passage 201.
- the refrigerant bleeding passage 202 is closed in response to the opening of the capacity control passage 201 when the compressor discharge pressure results predetermined high pressure state.
- the refrigerant is released from the discharge chamber 120 into the driving chamber 110 through the heating circuit capacity control passage 201.
- the refrigerant released into the driving chamber 110 can not be released into the suction chamber 115 because the refrigerant bleeding passage is closed by the refrigerant bleeding valve 185.
- the necessary steps for alleviating the abnormally high discharge pressure i.e., to increase the pressure within the driving chamber 110, to decrease the stroke length of the pistons 135, to decrease the compressor output discharge capacity and to decrease the compressor discharge pressure, can be taken extremely quickly.
- the refrigerant bleeding passage 202 by closing the refrigerant bleeding passage 202, the high-pressure refrigerant can be fully retained within the driving chamber. Therefore, the necessary amount of the refrigerant to increase the pressure within the driving chamber can be extremely reduced thereby minimizing the reduction of energy efficiency in operating the air conditioning system.
- a second representative embodiment is shown in FIG.4 and includes a driving chamber decompression passage 403 and a driving chamber decompression valve 409.
- the driving chamber decompression passage 403 connects the driving chamber 110 to the suction chamber 115 separately from the refrigerant bleeding passage 202.
- the driving chamber decompression valve 409 is provided within the driving chamber decompression passage 403.
- the driving chamber 110 is connected with a first chamber 413 provided within the driving chamber decompression valve 409 through a first driving chamber decompression passage 405. Therefore, pressure within the first chamber 413 is equal to the pressure Pc within the driving chamber 110.
- the suction chamber 115 is connected with a second chamber 415 provided within the driving chamber decompression valve 409 through a second driving chamber decompression passage 407.
- the pressure within the second chamber 415 is equal to the suction pressure Ps.
- the first chamber 413 and the second chamber 415 can be communicated with each other.
- a valve body 411 biased by a spring 417 cuts the communication between the first and second chambers 413, 415.
- the pressure within the first chamber 413 is also increased.
- Such high pressure within the first chamber prevails over the biasing force of the spring 417 and the pressure Ps within the second chamber 415.
- the valve body 411 moves to open the driving chamber decompression passage 403 (the valve body 411 moves upward in FIG.4).
- the high-pressure refrigerant within the driving chamber 110 is released into the suction chamber 115 through the driving chamber decompression passage 403 and the pressure Pc within the driving chamber 110 is decreased thereby preventing the airtight seal of the driving chamber from being degraded.
- the driving chamber decompression passage 403 and the driving chamber decompression valve 409 may be provided to the air conditioning system in association with the refrigerant bleeding valve that narrows or closes the refrigerant bleeding passage 202.
- the driving chamber decompression passage 403 and the driving chamber decompression valve 409 may be provided, as an emergent means, to the air conditioning system in association with the refrigerant bleeding valve that closes the refrigerant bleeding passage 202, because the driving chamber 110 is likely brought into the extremely high pressure state when the refrigerant bleeding passage 202 is closed.
- the refrigerant released from the discharge chamber 120 into the driving chamber 110 is to be utilized to increase the pressure within the driving chamber 110 for alleviating the abnormally high discharge pressure
- the refrigerant within the driving chamber 110 is to be released into the suction chamber 115 through the driving chamber decompression passage 403 only when the pressure within the driving chamber 110 results abnormally high pressure state as to degrade the driving chamber airtight seal.
- the condition for opening the driving chamber decompression valve 409 is set by adjusting the biasing force of the spring 417 such that only high pressure that exceeds the upper tolerance level of the driving chamber 110 moves the valve body 411 to open the driving chamber decompression valve 409.
- suction pressure Ps is utilized as one of the differential pressure to open or close the driving chamber decompression valve 409, another pressure such like atmospheric pressure or vacuum pressure may preferably be utilized in combination with the pressure Pc within the driving chamber.
- the air conditioning system has the cooling circuit and the heating circuit
- the cooling circuit may be omitted because it is mainly during operation of the heating circuit that the measure against the abnormally high discharge pressure is necessary.
- variable displacement compressor i.e., a variable displacement compressor of a type in which the pistons 135 are disposed only on one side of the swash plate 130 in FIGS. 3 and 4 is used in both of the first and second embodiments
- a double-ended piston type of compressor in which pistons are connected to opposite sides of the swash plate for reciprocation can be used.
- the capacity controller is provided inside the compressor (within the housing) in both of the first and second embodiments, the capacity controller can be provided outside the compressor.
- the air conditioning system 100 may include a compressor 101, a heating circuit 152, and a capacity controller 181.
- the compressor 101 has a suction port 115, a discharge port 120, a driving unit 130 provided within a driving chamber 110, a first passage 201 and a second passage 202.
- the driving unit 130 may decrease compressor output discharge capacity when the pressure within the driving chamber 110 increases.
- the first passage 201 may connect the discharge port 120 to the driving chamber 110 and the second passage 202 may connect the driving chamber 110 to the suction port 115.
- the capacity controller 181, 185 may open the first passage 201 when the refrigerant discharge pressure results predetermined pressure. Further, the capacity controller 181, 185 may narrow the second passage 202 in response to the opening of the first passage 201.
- the high-pressure refrigerant may be released from the discharge port 120 to the driving chamber 110 through the first passage 201.
- the second passage 202 By narrowing the second passage 202, the high-pressure refrigerant released from the discharge port is difficult to be released from the driving chamber 110 to the suction port 116.
- the pressure within the driving chamber 110 may quickly increase, the compressor output discharge capacity can be quickly reduced, the abnormally high discharge pressure of the compressor 101 can be quickly alleviated by the reduction in the compressor output discharge capacity.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Air-Conditioning For Vehicles (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP36316798 | 1998-12-21 | ||
JP10363167A JP2000177375A (ja) | 1998-12-21 | 1998-12-21 | 空調装置 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1014016A2 true EP1014016A2 (fr) | 2000-06-28 |
EP1014016A3 EP1014016A3 (fr) | 2002-01-16 |
Family
ID=18478663
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99125415A Withdrawn EP1014016A3 (fr) | 1998-12-21 | 1999-12-20 | Systèmes de conditionnement d'air |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1014016A3 (fr) |
JP (1) | JP2000177375A (fr) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1113235A1 (fr) * | 1999-12-27 | 2001-07-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Système de conditionnement d'air |
WO2002002942A1 (fr) * | 2000-07-06 | 2002-01-10 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Dispositif de securite pour compresseur de conditionnement d'air |
WO2002002940A1 (fr) * | 2000-07-06 | 2002-01-10 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Dispositif de securite pour compresseur de conditionnement d'air |
EP1291523A3 (fr) * | 2001-09-05 | 2005-06-01 | Kabushiki Kaisha Toyota Jidoshokki | Soupape de contrôle pour compresseur à capacité variable |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0719630A (ja) | 1993-07-02 | 1995-01-20 | Nippondenso Co Ltd | 空調装置 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61286591A (ja) * | 1985-06-13 | 1986-12-17 | Toyoda Autom Loom Works Ltd | 可変容量圧縮機 |
JPH04301189A (ja) * | 1991-03-28 | 1992-10-23 | Nippondenso Co Ltd | 冷房用可変容量コンプレッサ |
JPH04303185A (ja) * | 1991-03-29 | 1992-10-27 | Nippondenso Co Ltd | 斜板型可変容量圧縮機 |
JPH04321779A (ja) * | 1991-04-22 | 1992-11-11 | Nippondenso Co Ltd | 斜板型可変容量圧縮機 |
JP3237187B2 (ja) * | 1991-06-24 | 2001-12-10 | 株式会社デンソー | 空調装置 |
JP3024315B2 (ja) * | 1991-10-16 | 2000-03-21 | 株式会社豊田自動織機製作所 | 可変容量圧縮機 |
JP3131015B2 (ja) * | 1992-04-03 | 2001-01-31 | 株式会社鷺宮製作所 | 電磁式制御弁 |
JP3094725B2 (ja) * | 1993-03-29 | 2000-10-03 | 株式会社豊田自動織機製作所 | 可変容量型圧縮機 |
JP3678824B2 (ja) * | 1995-12-14 | 2005-08-03 | 株式会社テージーケー | 容量可変圧縮機の容量制御装置 |
US6010312A (en) * | 1996-07-31 | 2000-01-04 | Kabushiki Kaisha Toyoda Jidoshokki Seiksakusho | Control valve unit with independently operable valve mechanisms for variable displacement compressor |
-
1998
- 1998-12-21 JP JP10363167A patent/JP2000177375A/ja active Pending
-
1999
- 1999-12-20 EP EP99125415A patent/EP1014016A3/fr not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0719630A (ja) | 1993-07-02 | 1995-01-20 | Nippondenso Co Ltd | 空調装置 |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1113235A1 (fr) * | 1999-12-27 | 2001-07-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Système de conditionnement d'air |
US6449971B1 (en) | 1999-12-27 | 2002-09-17 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Air-conditioning system |
WO2002002942A1 (fr) * | 2000-07-06 | 2002-01-10 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Dispositif de securite pour compresseur de conditionnement d'air |
WO2002002940A1 (fr) * | 2000-07-06 | 2002-01-10 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Dispositif de securite pour compresseur de conditionnement d'air |
FR2811723A1 (fr) * | 2000-07-06 | 2002-01-18 | Luk Fahrzeug Hydraulik | Dispositif de securite pour compresseur de climatisation |
FR2812038A1 (fr) * | 2000-07-06 | 2002-01-25 | Luk Fahrzeug Hydraulik | Dispositif de securite pour compresseur de climatisation |
US6953325B2 (en) | 2000-07-06 | 2005-10-11 | Luk Fahrzeug-Hydraulik Gmbh & Co., Kg | Safety device to limit pressure in an axial-piston compressor housing |
EP1291523A3 (fr) * | 2001-09-05 | 2005-06-01 | Kabushiki Kaisha Toyota Jidoshokki | Soupape de contrôle pour compresseur à capacité variable |
Also Published As
Publication number | Publication date |
---|---|
EP1014016A3 (fr) | 2002-01-16 |
JP2000177375A (ja) | 2000-06-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6263687B1 (en) | Air conditioning systems | |
EP0952412B1 (fr) | Système frigorifique et procédé pour son fonctionnement | |
US6293117B1 (en) | Air conditioning system | |
US5531572A (en) | Capacity control valve for a variable capacity refrigerant compressor | |
EP0309242B1 (fr) | Système frigorifique muni d'un compresseur avec un mécanisme de déplacement variable commandé du dedans et du dehors | |
US6595015B2 (en) | Air conditioning systems | |
US6247322B1 (en) | Air conditioning systems | |
US6250093B1 (en) | Air conditioning system and compressor | |
JP2000318436A (ja) | 車輌用バイパス管路付冷凍サイクル | |
US6212893B1 (en) | Air conditioning systems | |
US6250094B1 (en) | Air conditioning systems | |
US20020104327A1 (en) | Vehicular air conditioner | |
EP1014016A2 (fr) | Systèmes de conditionnement d'air | |
EP1479907B1 (fr) | Dispositif de dérivation dans un compresseur à déplacement variable | |
EP1020692A2 (fr) | Systèmes de conditionnement d'air | |
EP1001230A2 (fr) | Systèmes de conditionnement d'air | |
JPH10153171A (ja) | 両頭ピストン式可変容量型圧縮機 | |
JP3187588B2 (ja) | 車両用空調装置 | |
JP3187587B2 (ja) | 車両用空調装置 | |
JP4118413B2 (ja) | 容量可変斜板式コンプレッサ | |
JPH0741359U (ja) | 自動車用空気調和装置 | |
JP2000205668A (ja) | 空調装置 | |
JPH10220350A (ja) | 可変容量型圧縮機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 19991220 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE Kind code of ref document: A2 Designated state(s): DE FR IT |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
AKX | Designation fees paid |
Free format text: DE FR IT |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20020702 |