US3894561A - Four-way reversing valve with differential area operator - Google Patents

Four-way reversing valve with differential area operator Download PDF

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US3894561A
US3894561A US45098474A US3894561A US 3894561 A US3894561 A US 3894561A US 45098474 A US45098474 A US 45098474A US 3894561 A US3894561 A US 3894561A
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chamber
valve
pressure
piston
pistons
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James M Thornbery
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Eaton Corp
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Controls Company of America
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Priority to US05450984 priority Critical patent/US3894561A/en
Priority to FR7507710A priority patent/FR2264234A1/fr
Priority to IT2124675A priority patent/IT1034264B/en
Priority to DE19752511370 priority patent/DE2511370A1/en
Priority to JP3102675A priority patent/JPS50127232A/ja
Priority to ES435623A priority patent/ES435623A1/en
Application granted granted Critical
Publication of US3894561A publication Critical patent/US3894561A/en
Priority to US05/703,840 priority patent/USRE30076E/en
Assigned to CONTROLS COMPANY OF AMERICA, 9655 W. SORENG AVENUE, SCHILLER PARK, IL., A CORP. OF DE. reassignment CONTROLS COMPANY OF AMERICA, 9655 W. SORENG AVENUE, SCHILLER PARK, IL., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SINGER COMPANY, THE
Assigned to EATON CORPORATION, A CORP. OF OH. reassignment EATON CORPORATION, A CORP. OF OH. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CONTROLS COMPANY OF AMERICA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/0655—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with flat slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
    • F16K31/363—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor the fluid acting on a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86726—Valve with bypass connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86839—Four port reversing valves

Definitions

  • the four-way reversing valve is utilized in refrigerating [2!] App! 0384 systems for heat pump applications to interchange the heating and cooling effects of the evaporator and conl52] US. Cl. 137/6252); l37/625.43; 251/3l denser.
  • the three-way pilot valve controls application [5 1] Int. Cl. H F16k 31/363 of high or low system pressure to the end of the cham- [58] Field of Search ]37/625,29 599,1, 62543; ber adjacent the large piston.
  • the two pistons result in movement of the slide valve to the left (both modifications) when high pressure is [56] R fe Cit d applied and to the right when low pressure is applied.
  • the object of this invention is to provide a four-way valve which is reliable in operation. competitive in cost. has tolerance to system dirt. and can be manufactured easily with reduced tolerance requirements.
  • FIG. 4 is a section on line 44 of FIG. 3 (but can be considered a similar section in FIG. I).
  • compressor It delivers hot refrigerant through conduit 12 to the slide valve chamber 14 in the reversing valve body 16. With the slide valve 18 in the position shown, the hot gas is delivered to outlet 20 and conduit 22 leading to the condenser 24.
  • Flow from the condenser 24 may be regulated by any suitable valve 26 to the evaporator 28 and flow from the evaporator goes through conduit 30 to port 32 below the slide valve 18 with the slide valve directing the flow to outlet 34 for return to the compressor 10 through conduit 36. Under these conditions the condenser 24 is hot and the evaporator 28 is cold.
  • the functions of the evaporator and condenser are reversed with the result that the formerly cold evaporator becomes hot and thus is suitable for heating the space rather than cooling the space.
  • the reversing valve I6 has a central chamber 14 in which the slide valve 18 is mounted.
  • the operation of the slide valve is controlled by the two pistons 38, which are of unequal size and interconnected for movement as a unit.
  • Pressure in chamber 42 between the piston 40 and the cylinder head is supplied through conduit 44 from either the high pressure or low pressure in accordance with the position of the three-way valve 46.
  • high pressure is supplied from conduit 12 through conduit 48, the three way valve 46, and conduit 44.
  • high pressure acts on both sides of piston 40 in the position shown in FIG. 1 with no net force tending to move piston 40.
  • three-way valve 46 When three-way valve 46 is actuated, low pressure is supplied to chamber 42 from conduit 36 through conduit 52, the three-way valve 46 and conduit 44. This results in a net force across piston 40 urging it to the right.
  • the left end of the valve body 16 is provided with a reduced diameter cylinder 54 with chamber 56 between piston 38 and cylinder head 58.
  • the pressure in chamber 56 is always at low pressure conditions, being connected to conduit 36 through conduit 60.
  • the two pistons are interconnected by the rod 62 which has an oblate portion 64 straddling slide valve 18 and connecting the rod to the valve so the piston motion will be transferred to the valve.
  • An oblate spring 66 underlies rod portion 64 with the spring being in the general shape of an M as seen in FIG. I.
  • the ends of the spring bear against the ledges 68 at either end of the slide valve and the two humps of the spring bear against the underside of the rod 64 so the slide valve 18 is held against the flat surface 70 through which the ports 32, 34 and 20 are bored.
  • the size of the cavity 72 in the slide valve and the projection of ledges 68 are important to achieve proper timing of the valve to prevent the system pressure being equalized during movement of the valve. Should that occur, the actuating forces on the piston assembly would be neutralized and the valve would hang up.
  • the net effect is a pressure derived force actuating interconnected pistons and the slide valve I8 to the right so that flow to the condenser 24 and evaporator 28 is reversed resulting in a reversal of function so the evaporator 28, which was cold. now becomes hot and can be used for heating a space rather than cooling the space.
  • Both piston heads are provided with bosses or pads 37, 41 (small and large pistons, respectively) which engage the cylinder heads to act as stops limiting movement of the piston assembly.
  • FIG. 3 The modification of FIG. 3 is not as desirable as that of FIG. I because it is more expensive to manufacture, but it illustrates the fact that there are variations possible in the construction.
  • the small diameter piston I38 and the large diameter piston 140 are interconnected by spindle with the chamber 94 at low system pressure supplied by conduit 96.
  • the larger diameter cylinder 92 is mounted on the right end of the main body 16 with ring 93 interconnecting the two. Flange 91 of the spindle 90 engages the ring 93 as illustrated in FIG. 3 to limit the movement of the piston assembly to the left.
  • Low pressure is provided to chamber 94 through conduit 96 at all times and can be communicated to chamber 142 between piston I40 and cylinder head 102 if the position of the three-way valve 46 is reversed from that illustrated.
  • high side pressure is communicated through conduit I48, the three-way valve 46, and conduit 144 to chamber 142. This, then, has a high side pressure acting in chamber 142 as well as in slide valve chamber 114.
  • the low pressure in chamber 94 is of no effect and, therefore, the net force acting on the piston assembly is to the left to the position shown.
  • the piston assembly is connected to the slide valve friction material pad 100 which prevents deflection of the rod under the force of spring 166 which acts between rod 162 and the slide valve 18 in the same manner as in FIG. 1.
  • the pressure differential required to initiate movement is about l psi which is readily attainable in an operating refrigerant system.
  • the force which must be overcome is the static friction load.
  • a reversing valve comprising,
  • a body including a valve chamber, a high pressure inlet to the chamber, a low pressure outlet from the chamber, and a pair of ports adjacent the outlet,
  • a slide valve in the chamber movable between two positions in which it serves to connect either of said ports to said outlet while the other port communicates with the chamber
  • said body including a large diameter cylinder and a small diameter cylinder
  • valve chamber is between the pistons.
  • a valve according to claim 1 in which both pistons are located at one end of the valve chamber and the space between the pistons is at low pressure.
  • a body including a valve chamber
  • a slide valve in the chamber movable between two positions in which either of the two ports comm unicates with said outlet while the other port communicates with the chamber to direct high pressure flowto the associated coil
  • said body including two cylinders of unequal size

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Multiple-Way Valves (AREA)
  • Air Conditioning Control Device (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

The four-way reversing valve is utilized in refrigerating systems for heat pump applications to interchange the heating and cooling effects of the evaporator and condenser. The three-way pilot valve controls application of high or low system pressure to the end of the chamber adjacent the large piston. The different areas of the two pistons result in movement of the slide valve to the left (both modifications) when high pressure is applied and to the right when low pressure is applied.

Description

United States Patent [191 Thornbery July 15, 1975 FOUR-WAY REVERSING VALVE WITH DIFFERENTIAL AREA OPERATOR 3,448,959 6/1969 McHale et al. 137/62529 X [75] Inventor: James M. Thornbery, Milwaukee, Primary Examiner-Arnold Rosenthal Wis. Attorney. Agenl, r FirmMichael, Best & Friedrich [73] Assignee; Controls Company of America,
S hll P k, Illv C 57 ABSTRACT [22] Filed; Mar. 14.1974
I The four-way reversing valve is utilized in refrigerating [2!] App! 0384 systems for heat pump applications to interchange the heating and cooling effects of the evaporator and conl52] US. Cl. 137/6252); l37/625.43; 251/3l denser. The three-way pilot valve controls application [5 1] Int. Cl. H F16k 31/363 of high or low system pressure to the end of the cham- [58] Field of Search ]37/625,29 599,1, 62543; ber adjacent the large piston. The different areas of [/3| the two pistons result in movement of the slide valve to the left (both modifications) when high pressure is [56] R fe Cit d applied and to the right when low pressure is applied.
UNITED STATES PATENTS 2,920,653 1/1960 Wolff 137/5991 x 4 Clams 4 Drawmg figures M a8 Z a; z
a do -e2 06 l \JZ Q 22 FOUR-WAY REVERSING VALVE WITH DIFFERENTIAL AREA OPERATOR BACKGROUND OF THE INVENTION Reversing valves for heat pump systems are old with the most successful design being that shown in US. Pat. No. 2,976,7OI. That design relies upon a controlled leakage and can be disabled by dirt. The design requires careful manufacture.
SUMMARY OF THE INVENTION The object of this invention is to provide a four-way valve which is reliable in operation. competitive in cost. has tolerance to system dirt. and can be manufactured easily with reduced tolerance requirements.
DESCRIPTION OF THE DRAWINGS FIG. 4 is a section on line 44 of FIG. 3 (but can be considered a similar section in FIG. I).
DESCRIPTION OF THE PREFERRED EMBODIMENTS In the system shown in FIG. I compressor It) delivers hot refrigerant through conduit 12 to the slide valve chamber 14 in the reversing valve body 16. With the slide valve 18 in the position shown, the hot gas is delivered to outlet 20 and conduit 22 leading to the condenser 24. Flow from the condenser 24 may be regulated by any suitable valve 26 to the evaporator 28 and flow from the evaporator goes through conduit 30 to port 32 below the slide valve 18 with the slide valve directing the flow to outlet 34 for return to the compressor 10 through conduit 36. Under these conditions the condenser 24 is hot and the evaporator 28 is cold. When the flow is reversed, as explained more fully hereafter, the functions of the evaporator and condenser are reversed with the result that the formerly cold evaporator becomes hot and thus is suitable for heating the space rather than cooling the space.
The reversing valve I6 has a central chamber 14 in which the slide valve 18 is mounted. The operation of the slide valve is controlled by the two pistons 38, which are of unequal size and interconnected for movement as a unit. Pressure in chamber 42 between the piston 40 and the cylinder head is supplied through conduit 44 from either the high pressure or low pressure in accordance with the position of the three-way valve 46. In the position shown, high pressure is supplied from conduit 12 through conduit 48, the three way valve 46, and conduit 44. Thus high pressure acts on both sides of piston 40 in the position shown in FIG. 1 with no net force tending to move piston 40. When three-way valve 46 is actuated, low pressure is supplied to chamber 42 from conduit 36 through conduit 52, the three-way valve 46 and conduit 44. This results in a net force across piston 40 urging it to the right.
The left end of the valve body 16 is provided with a reduced diameter cylinder 54 with chamber 56 between piston 38 and cylinder head 58. The pressure in chamber 56 is always at low pressure conditions, being connected to conduit 36 through conduit 60. The two pistons are interconnected by the rod 62 which has an oblate portion 64 straddling slide valve 18 and connecting the rod to the valve so the piston motion will be transferred to the valve. An oblate spring 66 underlies rod portion 64 with the spring being in the general shape of an M as seen in FIG. I. The ends of the spring bear against the ledges 68 at either end of the slide valve and the two humps of the spring bear against the underside of the rod 64 so the slide valve 18 is held against the flat surface 70 through which the ports 32, 34 and 20 are bored. It should be noted that the size of the cavity 72 in the slide valve and the projection of ledges 68 are important to achieve proper timing of the valve to prevent the system pressure being equalized during movement of the valve. Should that occur, the actuating forces on the piston assembly would be neutralized and the valve would hang up.
In the position shown in FIG. I, there is equal pressure on each side of piston 40 as noted before. There is a pressure differential across the small piston 38. however. with high side pressure in chamber I4 and low side pressure in chaamber 56. Therefore. the small piston has a force acting on it moving it left and the pis ton assembly is held in the position shown. If the threeway valve 46 is actuated to provide low pressure to the chamber 42, there is now high to low pressure acting across piston 40 just as there is across the small piston 38. Since the large piston has approximately twice the area of the small piston, the net effect is a pressure derived force actuating interconnected pistons and the slide valve I8 to the right so that flow to the condenser 24 and evaporator 28 is reversed resulting in a reversal of function so the evaporator 28, which was cold. now becomes hot and can be used for heating a space rather than cooling the space.
Both piston heads are provided with bosses or pads 37, 41 (small and large pistons, respectively) which engage the cylinder heads to act as stops limiting movement of the piston assembly.
The modification of FIG. 3 is not as desirable as that of FIG. I because it is more expensive to manufacture, but it illustrates the fact that there are variations possible in the construction. In this arrangement the small diameter piston I38 and the large diameter piston 140 are interconnected by spindle with the chamber 94 at low system pressure supplied by conduit 96. The larger diameter cylinder 92 is mounted on the right end of the main body 16 with ring 93 interconnecting the two. Flange 91 of the spindle 90 engages the ring 93 as illustrated in FIG. 3 to limit the movement of the piston assembly to the left.
Low pressure is provided to chamber 94 through conduit 96 at all times and can be communicated to chamber 142 between piston I40 and cylinder head 102 if the position of the three-way valve 46 is reversed from that illustrated. As illustrated, high side pressure is communicated through conduit I48, the three-way valve 46, and conduit 144 to chamber 142. This, then, has a high side pressure acting in chamber 142 as well as in slide valve chamber 114. The low pressure in chamber 94 is of no effect and, therefore, the net force acting on the piston assembly is to the left to the position shown.
The piston assembly is connected to the slide valve friction material pad 100 which prevents deflection of the rod under the force of spring 166 which acts between rod 162 and the slide valve 18 in the same manner as in FIG. 1.
If the three-way valve is now actuated, low pressure will be supplied to chamber 142. This results in a net effect of the high pressure in chamber 114 acting against low pressure in chamber 142 and, therefore, the valve assembly will move to the right to the limit determined by engagement of the boss [41 with the cylinder head 102.
The pressure differential required to initiate movement is about l psi which is readily attainable in an operating refrigerant system. The force which must be overcome is the static friction load.
I claim:
l. A reversing valve comprising,
a body including a valve chamber, a high pressure inlet to the chamber, a low pressure outlet from the chamber, and a pair of ports adjacent the outlet,
a slide valve in the chamber movable between two positions in which it serves to connect either of said ports to said outlet while the other port communicates with the chamber,
said body including a large diameter cylinder and a small diameter cylinder,
a piston in each cylinder, the pistons being interconnected and being connected to the slide valve,
means supplying a constant pressure to the space between the pistons.
one side of the smaller piston being exposed to the chamber pressure and the other side of the smaller piston being exposed to low pressure so there is always a pressure differential acting across the smaller piston,
means supplying high or low pressure to the space between the larger piston and the head of the larger cylinder to cause the pistons and slide valve to move between said positions by reason of the pressure differential acting across the small piston area in one position and by reason of the pressure differential across the difference in piston areas in the other position.
2. A valve according to claim 1 in which the valve chamber is between the pistons.
3. A valve according to claim 1 in which both pistons are located at one end of the valve chamber and the space between the pistons is at low pressure.
4. The combination with a refrigeration system of the heat pump type in which the compressor delivers hot high pressure refrigerant to a reversing valve which directs flow to one of two coils to be condensed therein and then metered into the other of the coils from which the refrigerant flows through the reversing valve at low pressure for return to the compressor, of an improved reversing valve, comprising,
a body including a valve chamber,
an inlet to the chamber connected to the compressor outlet whereby high system pressure obtains in the chamber,
an outlet from the chamber connected to the compressor suction line,
a pair of ports in the chamber, each being connected to one of the coils,
a slide valve in the chamber movable between two positions in which either of the two ports comm unicates with said outlet while the other port communicates with the chamber to direct high pressure flowto the associated coil,
said body including two cylinders of unequal size,
a piston in each cylinder, the pistons being interconnected and connected to the slide valve,
the space between the pistons being at a system pressure,
one side of the smaller piston being exposed to high system pressure in the valve chamber,
and means for connecting the space between the larger piston and its associated cylinder head to either high or low system pressure to actuate the pistons and slide valve.
@3 3 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,894 561 Dated July 15, 1.975
Inventor(s) James M. Thornbery It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:
Column 4, delete claim 4.
On the Cover Sheet, after the Abstract,"'4 Claims" should read H 3 Claims Signed and Scaled this sixth D y of January 1976 [SEAL] Arrest:
RUTH C. MASON C. MARSHALL DANN Arresting Officer Commissioner of Parents and Trademarks

Claims (4)

1. A reversing valve comprising, a body including a valve chamber, a high pressure inlet to the chamber, a low pressure outlet from the chamber, and a pair of ports adjacent the outlet, a slide valve in the chamber movable between two positions in which it serves to connect either of said ports to said outlet while the other port communicates with the chamber, said body including a large diameter cylinder and a small diameter cylinder, a piston in each cylinder, the pistons being interconnected and being connected to the slide valve, means supplying a constant pressure to the space between the pistons, one side of the smaller piston being exposed to the chamber pressure and the other side of the smaller piston being exposed to low pressure so there is always a pressure differential acting across the smaller piston, means supplying high or low pressure to the space between the larger piston and the head of the larger cylinder to cause the pistons and slide valve to move between said positions by reason of the pressure differential acting across the small piston area in one position and by reason of the pressure differential across the difference in piston areas in the other position.
2. A valve according to claim 1 in which the valve chamber is between the pistons.
3. A valve according to claim 1 in which both pistons are located at one end of the valve chamber and the space between the pistons is at low pressure.
4. The combination with a refrigeration system of the heat pump type in which the compressor delivers hot high pressure refrigerant to a reversing valve which directs flow to one of two coils to be condensed therein and then metered into the other of the coils from which the refrigerant flows through the reversing valve at low pressure for return to the compressor, of an improved reversing valve, comprising, a body including a valve chamber, an inlet to the chamber connected to the compressor outlet whereby high system pressure obtains in the chamber, an outlet from the chamber connected to the compressor suction line, a pair of ports in the chamber, each being connected to one of the coils, a slide valve in the chamber movable between two positions in which either of the two ports communicates with said outlet while the other port communicates with the chamber to direct high pressure flow to the associated coil, said body including two cylinders of unequal size, a piston in each cylinder, the pistons being interconnected and connected to the slide valve, the space between the pistons being at a system pressure, one side of the smaller piston being exposed to high system pressure in the valve chamber, and means for connecting the space between the larger piston and its associated cylinder head to either high or low system pressure to actuate the pistons and slide valve.
US05450984 1974-03-14 1974-03-14 Four-way reversing valve with differential area operator Expired - Lifetime US3894561A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US05450984 US3894561A (en) 1974-03-14 1974-03-14 Four-way reversing valve with differential area operator
FR7507710A FR2264234A1 (en) 1974-03-14 1975-03-12
IT2124675A IT1034264B (en) 1974-03-14 1975-03-13 INVERSION VALVE IN PARTICULAR FOR COMPRESSOR OF FRIEGERANT SYSTEMS
JP3102675A JPS50127232A (en) 1974-03-14 1975-03-14
DE19752511370 DE2511370A1 (en) 1974-03-14 1975-03-14 REVERSING SLIDER
ES435623A ES435623A1 (en) 1974-03-14 1975-03-14 Four-way reversing valve with differential area operator
US05/703,840 USRE30076E (en) 1974-03-14 1976-07-09 Four-way reversing valve with differential area operator

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US05450984 US3894561A (en) 1974-03-14 1974-03-14 Four-way reversing valve with differential area operator

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US05/703,840 Reissue USRE30076E (en) 1974-03-14 1976-07-09 Four-way reversing valve with differential area operator

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US3894561A true US3894561A (en) 1975-07-15

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US (1) US3894561A (en)
JP (1) JPS50127232A (en)
DE (1) DE2511370A1 (en)
ES (1) ES435623A1 (en)
FR (1) FR2264234A1 (en)
IT (1) IT1034264B (en)

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4144905A (en) * 1977-08-19 1979-03-20 Robertshaw Controls Company Reversing valve construction and method of making the same
US4212324A (en) * 1978-11-15 1980-07-15 Robershaw Controls Company Reversing valve construction and method of making the same
US4248058A (en) * 1979-04-04 1981-02-03 Robertshaw Controls Company Differential piston type reversing valve construction, system utilizing the same and method of making
US4255939A (en) * 1979-05-21 1981-03-17 Emerson Electric Co. Four way reversing valve
US4406306A (en) * 1982-03-19 1983-09-27 Eaton Corporation Heat pump switchover valve
US4492252A (en) * 1981-03-18 1985-01-08 Kabushiki Kaisha Saginomiya Seisakusho Reversible valve for reversible refrigeration cycle
EP0173138A2 (en) * 1984-08-23 1986-03-05 Ranco Incorporated Refrigerant reversing valve
US4976286A (en) * 1989-12-14 1990-12-11 Automatic Switch Company Four-way slide valve
ES2079279A2 (en) * 1992-09-09 1996-01-01 Hitachi Ltd Air conditioner
US6063169A (en) * 1996-05-10 2000-05-16 Litton Systems, Inc. Control means for molecular sieve on-board oxygen generator
US6158466A (en) * 1999-01-14 2000-12-12 Parker-Hannifin Corporation Four-way flow reversing valve for reversible refrigeration cycles
EP1092928A1 (en) * 1998-07-02 2001-04-18 Kabushiki Kaisha Saginomiya Seisakusho Flow path selector valve and method of selecting and driving the valve, compressor with flow path selector valve, and refrigerating cycle control device
US6409807B1 (en) 2000-05-23 2002-06-25 Litton Systems, Inc. Linear gas valve cycle control, shut-off-valve and self test
EP1371889A3 (en) * 2002-06-13 2004-02-11 TGK Co., Ltd. Three-way switching valve
US6698452B2 (en) 2000-01-19 2004-03-02 Emerson Electric Co. Cycle reversing valve for use in heat pumps
CN100342139C (en) * 2003-09-30 2007-10-10 三星电子株式会社 Variable capacity rotary compressor
CN100346074C (en) * 2003-09-30 2007-10-31 三星电子株式会社 Variable capacity rotary compressor
CN100395453C (en) * 2003-09-19 2008-06-18 三星电子株式会社 Variable capacity rotary compressor
CN101319734B (en) * 2007-06-04 2010-09-22 浙江三花制冷集团有限公司 Piston link lever of four-way reversing valve
US20100307607A1 (en) * 2009-06-04 2010-12-09 James Glenn Ary Reversing valve
US20110088427A1 (en) * 2008-06-12 2011-04-21 Yutaka Ishii Control Valve and Air Conditioner Equipped with the Valve
CN101666386B (en) * 2009-09-18 2012-01-18 清华大学 Self-operated type three-way valve
CN102954243A (en) * 2011-08-29 2013-03-06 浙江三花制冷集团有限公司 Large four-way reversing valve and slide block component thereof
CN104634010A (en) * 2014-12-31 2015-05-20 浙江陆特能源科技股份有限公司 Construction technology for refrigerating and heating switching pipelines and switching system for refrigerating and heating switching pipelines
CN106032846A (en) * 2015-03-17 2016-10-19 浙江盾安禾田金属有限公司 Self-operated three-way valve and air-conditioning system thereof
CN106763894A (en) * 2015-11-24 2017-05-31 株式会社鹭宫制作所 Switching valve and freeze cycle
CN107237900A (en) * 2016-03-29 2017-10-10 珠海华宇金属有限公司 A kind of flat spring and four-way reversing valve
CN108253669A (en) * 2016-12-29 2018-07-06 杭州三花研究院有限公司 Mostly logical reversing arrangement and air-conditioning system
US20180299173A1 (en) * 2015-05-14 2018-10-18 Jhejiang Sanhua Climate And Appliance Controls Group., Ltd. Reversing valve and cooling system having same
CN111120690A (en) * 2018-10-31 2020-05-08 广东美芝精密制造有限公司 Four-way valve
CN111911661A (en) * 2019-05-07 2020-11-10 株式会社不二工机 Flow path switching valve
US10907748B2 (en) * 2016-03-30 2021-02-02 Ckd Corporation Flow path switching valve and manufacturing method therefor
US11268628B2 (en) 2017-12-25 2022-03-08 Ckd Corporation Electromagnetic actuator
WO2022161457A1 (en) * 2021-02-01 2022-08-04 浙江三花智能控制股份有限公司 Electromagnetic switching valve
US20230228334A1 (en) * 2020-09-25 2023-07-20 Zhejiang Dunan Artificial Environment Co., Ltd. Guide frame for four-way reversing valve
US20230358323A1 (en) * 2020-08-20 2023-11-09 Zhejiang Dunan Artificial Environment Co., Ltd. Valve Core Assembly and Reversing Valve with Valve Core Assembly

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US4144905A (en) * 1977-08-19 1979-03-20 Robertshaw Controls Company Reversing valve construction and method of making the same
US4212324A (en) * 1978-11-15 1980-07-15 Robershaw Controls Company Reversing valve construction and method of making the same
US4248058A (en) * 1979-04-04 1981-02-03 Robertshaw Controls Company Differential piston type reversing valve construction, system utilizing the same and method of making
US4255939A (en) * 1979-05-21 1981-03-17 Emerson Electric Co. Four way reversing valve
US4492252A (en) * 1981-03-18 1985-01-08 Kabushiki Kaisha Saginomiya Seisakusho Reversible valve for reversible refrigeration cycle
US4406306A (en) * 1982-03-19 1983-09-27 Eaton Corporation Heat pump switchover valve
EP0173138A2 (en) * 1984-08-23 1986-03-05 Ranco Incorporated Refrigerant reversing valve
EP0173138A3 (en) * 1984-08-23 1987-08-05 Ranco Incorporated Refrigerant reversing valve
US4976286A (en) * 1989-12-14 1990-12-11 Automatic Switch Company Four-way slide valve
FR2656061A1 (en) * 1989-12-14 1991-06-21 Automatic Switch Co VALVE WITH DRAWER AND FOUR WAYS.
BE1004131A5 (en) * 1989-12-14 1992-09-29 Automatic Switch Co Valve and drawer four-lane.
ES2079279A2 (en) * 1992-09-09 1996-01-01 Hitachi Ltd Air conditioner
US6063169A (en) * 1996-05-10 2000-05-16 Litton Systems, Inc. Control means for molecular sieve on-board oxygen generator
EP1092928A1 (en) * 1998-07-02 2001-04-18 Kabushiki Kaisha Saginomiya Seisakusho Flow path selector valve and method of selecting and driving the valve, compressor with flow path selector valve, and refrigerating cycle control device
EP1092928A4 (en) * 1998-07-02 2005-01-05 Saginomiyaseisakusho Kk Flow path selector valve and method of selecting and driving the valve, compressor with flow path selector valve, and refrigerating cycle control device
US6158466A (en) * 1999-01-14 2000-12-12 Parker-Hannifin Corporation Four-way flow reversing valve for reversible refrigeration cycles
US6698452B2 (en) 2000-01-19 2004-03-02 Emerson Electric Co. Cycle reversing valve for use in heat pumps
US6409807B1 (en) 2000-05-23 2002-06-25 Litton Systems, Inc. Linear gas valve cycle control, shut-off-valve and self test
EP1371889A3 (en) * 2002-06-13 2004-02-11 TGK Co., Ltd. Three-way switching valve
US6883545B2 (en) 2002-06-13 2005-04-26 Tgk Co., Ltd. Three-way switching valve
CN100395453C (en) * 2003-09-19 2008-06-18 三星电子株式会社 Variable capacity rotary compressor
CN100342139C (en) * 2003-09-30 2007-10-10 三星电子株式会社 Variable capacity rotary compressor
CN100346074C (en) * 2003-09-30 2007-10-31 三星电子株式会社 Variable capacity rotary compressor
CN101319734B (en) * 2007-06-04 2010-09-22 浙江三花制冷集团有限公司 Piston link lever of four-way reversing valve
US20110088427A1 (en) * 2008-06-12 2011-04-21 Yutaka Ishii Control Valve and Air Conditioner Equipped with the Valve
US8505580B2 (en) 2009-06-04 2013-08-13 Parker-Hannifin Corporation Reversing valve
US20100307607A1 (en) * 2009-06-04 2010-12-09 James Glenn Ary Reversing valve
CN101666386B (en) * 2009-09-18 2012-01-18 清华大学 Self-operated type three-way valve
CN102954243A (en) * 2011-08-29 2013-03-06 浙江三花制冷集团有限公司 Large four-way reversing valve and slide block component thereof
CN104634010A (en) * 2014-12-31 2015-05-20 浙江陆特能源科技股份有限公司 Construction technology for refrigerating and heating switching pipelines and switching system for refrigerating and heating switching pipelines
CN104634010B (en) * 2014-12-31 2018-02-16 浙江陆特能源科技股份有限公司 Cooling and warming switches the construction technology and its switching system of pipeline
CN106032846A (en) * 2015-03-17 2016-10-19 浙江盾安禾田金属有限公司 Self-operated three-way valve and air-conditioning system thereof
CN106032846B (en) * 2015-03-17 2019-12-24 浙江盾安禾田金属有限公司 Self-operated three-way valve and air conditioning system thereof
US20180299173A1 (en) * 2015-05-14 2018-10-18 Jhejiang Sanhua Climate And Appliance Controls Group., Ltd. Reversing valve and cooling system having same
US10619897B2 (en) * 2015-05-14 2020-04-14 Zhejiang Sanhua Climate And Appliance Controls Group., Ltd Reversing valve and cooling system having same
CN106763894A (en) * 2015-11-24 2017-05-31 株式会社鹭宫制作所 Switching valve and freeze cycle
CN106763894B (en) * 2015-11-24 2019-09-13 株式会社鹭宫制作所 Switching valve and refrigerating circulation system
CN107237900A (en) * 2016-03-29 2017-10-10 珠海华宇金属有限公司 A kind of flat spring and four-way reversing valve
US11566723B2 (en) 2016-03-30 2023-01-31 Ckd Corporation Flow path switching valve and manufacturing method therefor
US10907748B2 (en) * 2016-03-30 2021-02-02 Ckd Corporation Flow path switching valve and manufacturing method therefor
CN108253669A (en) * 2016-12-29 2018-07-06 杭州三花研究院有限公司 Mostly logical reversing arrangement and air-conditioning system
CN108253669B (en) * 2016-12-29 2021-10-19 杭州三花研究院有限公司 Multi-way reversing device and air conditioning system
US11268628B2 (en) 2017-12-25 2022-03-08 Ckd Corporation Electromagnetic actuator
CN111120690A (en) * 2018-10-31 2020-05-08 广东美芝精密制造有限公司 Four-way valve
CN111120690B (en) * 2018-10-31 2021-10-22 广东美芝精密制造有限公司 Four-way valve
CN111911661A (en) * 2019-05-07 2020-11-10 株式会社不二工机 Flow path switching valve
CN111911661B (en) * 2019-05-07 2024-04-16 株式会社不二工机 Flow path switching valve
US20230358323A1 (en) * 2020-08-20 2023-11-09 Zhejiang Dunan Artificial Environment Co., Ltd. Valve Core Assembly and Reversing Valve with Valve Core Assembly
US20230228334A1 (en) * 2020-09-25 2023-07-20 Zhejiang Dunan Artificial Environment Co., Ltd. Guide frame for four-way reversing valve
US12104708B2 (en) * 2020-09-25 2024-10-01 Zhejiang Dunan Artificial Environment Co., Ltd. Guide frame for four-way reversing valve
WO2022161457A1 (en) * 2021-02-01 2022-08-04 浙江三花智能控制股份有限公司 Electromagnetic switching valve

Also Published As

Publication number Publication date
FR2264234A1 (en) 1975-10-10
ES435623A1 (en) 1976-12-16
JPS50127232A (en) 1975-10-07
IT1034264B (en) 1979-09-10
DE2511370A1 (en) 1975-09-18

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