JPH02154879A - Selector valve - Google Patents

Abstract

PURPOSE:To obtain a simple selector valve with high energy efficiency by moving a pressure difference reacting means with a double piston structure having the first piston and the second piston via a solenoid operated by a thermostat. CONSTITUTION:A sleeve 37 is arranged in a housing 25, and a spool 46 with three pistons 47-49 is slidably arranged in it. When a solenoid 33 is de-excited, the refrigerant from a compressor 12 is fed to a selector valve through an input port 15, flows out through an outflow port 19 via an opening 43, passes heat exchangers 13 and 14 and is fed to the selector valve through a port 22, and is returned to the compressor 12 through an output port 17. When the preset temperature is attained and a thermostat is operated and the solenoid 33 is excited, the spool 46 is moved to the right, the refrigerant fed through the port 15 passes the port 22, flows in the opposite direction to the heat exchangers 14 and 13, and is returned to the compressor through the port 19 via the output port 17. The selector valve of a heat pump with a simple production process and high energy efficiency is obtained.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a fluid control valve, and more particularly to an improved fluid control valve for use in a heat pump system that selectively controls the direction of compressed refrigerant to perform a heating or cooling function. Regarding switching valves.

[Background of the invention]

Heat pump systems are well known for switching valves to control the direction of refrigerant flow. Conventional heat pump systems include a refrigerant compressor, an external heat exchanger, an internal heat exchanger, and a switching valve that selectively supplies compressed refrigerant to either heat exchanger. The aforementioned heat exchangers are capable of condensing and vaporizing refrigerant, respectively, and thus can perform heating or cooling functions depending on the flow direction of the refrigerant. The switching valve has an input port connected to the compressor output, a reflux port connected to the compressor input, and two reversible fluid ports connected to the external and internal heat exchangers. The switching valve selectively establishes a fluid path from the compressor output through the valve input port and the valve body to either of the two heat exchangers. The recirculated refrigerant is sent from the other heat exchanger via a valve to the input of the compressor. In the opposite case, the flow simply switches. That is, compressed refrigerant from the output of the compressor is sent to a second heat exchanger;
It is returned from the first heat exchanger to the input of the compressor via the valve body.

Diverter valves are commercially available in a variety of configurations, and many use the compressed refrigerant itself as the control or moving fluid to determine the position of the valve as a function of temperature, usually detected by the output of a thermostat. do.

The present invention relates to an improved switching valve that uses the compressed refrigerant itself to determine the position of the valve element as a function of temperature.

In the two embodiments described below, a dual piston structure differential pressure responsive means is provided having a first piston disposed in a first chamber and a second piston disposed in a second chamber. The functions described above are performed by The first chamber is maintained in constant communication with the compressed refrigerant output directly from the compressor. The second chamber is also in communication with compressed refrigerant from the output of the compressor, but the fluid passageway is narrow. Second
The chamber is provided with means for withdrawing fluid from the chamber, thus reducing the pressure in the chamber when a predetermined temperature limit is reached.

In the embodiment, a low voltage thermostat is connected to a solenoid located within the switching valve, and a plunger closes or opens the bleed path. As a result, the pressure in the second chamber is equal to or less than the pressure in the first chamber.

The two pistons have different surface areas, preferably the piston in the second chamber is twice as large as the piston in the first chamber. Therefore, when the bleed passage is closed, the pressure in both chambers is equal, but the larger piston moves the valve member into the first operating mode. When the temperature returns to the predetermined limit, the solenoid is actuated to open a bleed passage, reducing the pressure in the second chamber and placing the valve member in a second mode of operation by the force exerted on the piston in the first chamber. move it.

The valve body consists of a cylindrical housing with an elongated plastic molded sleeve inserted into the housing to provide various control passageways and fluid transfer functions. The sleeve is shaped with an irregularly shaped internal bore, and both the valve element and the differential pressure responsive means are movably disposed within the bore of the sleeve. The solenoid is mounted coaxially to one end of the valve housing, and the bleed passage in the second chamber is nozzle-shaped and coaxially arranged in the plunge of the solenoid. The switching valve configured in this manner is small and lightweight, and does not require any external parts such as a thermostat.

It is desirable that the diverter valve include a liner molded from polyesterimide resin to provide good stability and thermal insulation over the wide range of temperatures in which it will be used.

The use of a plastic molded sleeve not only forms all of the control passages and fluid transfer paths, but also significantly increases thermal insulation over a wide temperature range of the refrigerant during heating and cooling cycles. Therefore, the switching valve according to the present invention can achieve the effect of increasing energy efficiency.

In a first embodiment of the invention, the fluid withdrawn from the second chamber is returned to the suction line of the compressor through the valve body of the switching valve. In addition, the second embodiment is configured to remove the bleed function of the passage after the valve member shifts to the second operation mode, thereby reducing the amount of compressed refrigerant used in the valve control process. can be minimized.

In either embodiment, the diverter valve is small and lightweight, uses molded plastic components to simplify the manufacturing process, requires no external parts, is easy to install, and thermally directs the refrigerant. Because it is insulated, it has high energy efficiency.

〔Example〕

FIG. 1 is a sectional view of a switching valve of a heat pump according to the present invention, and the switching valve as a whole is designated by 11.

The switching valve 11 is included in the heat pump system.
In the figure, the heat pump system is represented schematically and consists of a refrigerant compressor 12 and a heat exchanger 13.14. The switching valve 11 includes an input port 15 and an output port 17. Input port 15 is connected to the output of compressor 12 via conduit 16, and output port 17 is connected to compressor 120 input via conduit 18. The switching valve 11 further includes a reversible flow port 19 connected to the heat exchanger 13 via a conduit 21 and a conduit 2.
Reversible flow port 22 connected to heat exchanger 14 via 3
It is equipped with The fluid loop of a heat pump system is
It is completed with conduits 24 interconnecting the heat exchangers 13,14.

The heat exchangers 13, 14 are capable of condensing or vaporizing the refrigerant and therefore can perform either heating or cooling functions depending on the direction of flow of the refrigerant. As is well known in the art, the switching valve 11 has a wide range of functions by selecting the flow of refrigerant. For example, compressor 12
from the output of the compressor 12 via the input port 15 to the port 19, the heat exchanger 13.14, the port 22 and then the output port 17 to the input of the compressor 12, or vice versa, from the input port 15 to the port 22, There are a heat exchanger 14, 13, a port 19, and a path for refluxing from the output port 17 to the compressor 12. Reversible flow heat pump systems are already well known and do not form part of the present invention, so further explanation will be omitted.

The switching valve 11 has a cylindrical closed housing 25. The housing 25 has a wide section 26 (shown as the left section in Figure 1) and a narrow section 27 (the right section).
They are separated. These portions 26 and 27 have connection flanges 26a and 27a on their peripheries, respectively, and are hermetically connected with a plurality of screws 29 with an annular gasket 28 in between. Therefore, when parts within the valve 11 are replaced, etc., the sections 26, 27 are separated. However, at the manufacturing stage, part 26
．． It is also possible to permanently seal 27. An opening 26b for receiving the input port 15 is formed at one end of the left side portion 26, a coaxial opening 26c for the port 17 is formed at the end, and openings 26d and 26e for the port 19.22 are formed on the opposite side. .

In this embodiment, the two parts 26.27 of the housing are made of drawn sheet steel, and the steel ports 15.17.19.22 are welded with copper to the corresponding openings 26b-26e.

Similarly, the cylindrical solenoid housing 31 is located on the right side 2.
7, and is fixed as described below. Each connection is provided with an O-ring 32 to prevent leakage.

An opening 27b is formed at the right end of the right side portion 27, and a stainless steel pipe 40 with a flange on the left side surrounds this opening 27b and is welded to the end of the right side portion 27 so as to protrude to the right side in the figure. . The solenoid 33 consists of an annular coil 33a with a hollow center, and is supported by a tube 40 so as to be able to slide.

A movable core or plunger 34 is slidably disposed within the tube 40 and extends through the opening 27b into the interior of the right portion 27. A compression spring 35 is disposed between the plunger 34 and the fixed core 33b, and normally biases the plunger 34 in the extending direction shown in FIG. At this time, the solenoid 33 is in a deenergized state.

A threaded stud 33c secured to the closed right end of the tube 40 extends coaxially through the end of the solenoid housing 31 and is secured to the solenoid housing 31 by a bolt 33d. With this structure, by removing the nut 33d and the solenoid housing 31, the solenoid 33 and its related parts can be seen.

The housing 31 is pulled out from the solenoid coil 33a.
A low voltage wire 36 passing through is connected to an electrical thermostat (not shown). The thermostat generates an electrical signal when a predetermined temperature limit is reached, activating the solenoid 33 and retracting the plunger 34. The operation of the switching valve 11 according to this state will be described in detail below.

Housing 25 forms an elongated cylindrical chamber.

This chamber has a coaxial opening 2 which receives the input and output ports 15, 17, 19, 22 and the solenoid plunger 34.
It is sealed except for 7b. Disposed within the cylindrical chamber is a plastic molded sleeve or liner 37 having a generally cylindrical outer surface and sized to fit hermetically within the cylindrical housing 25. -For boat fishing,
Sleeve 37 includes an irregularly shaped coaxial perforated cylindrical member, as will be described below. In this embodiment, the sleeve 37 is molded into two connectable parts. However, for clarity, the figures are shown as a single piece.

More specifically, the sleeve 37 has a large annular recess 39 formed on the left end side in FIG. The recess 39 is disposed in line with the reversible flow port 19 and communicates with the coaxial hole 38 through a plurality of openings 41 . Similarly, a large annular recess is formed in the center of the sleeve 37 in line with the input port 15, and a coaxial hole 38 is formed through the opening 43.
Communicate with.

The sleeve 37 is provided with a plurality of annular grooves for attaching O-rings 40a to 40d.
This prevents refrigerant from leaking between the housing 25 and the cylindrical housing 25. Specifically, the 0-ring 40a is between the port 19 and the coaxial port 17, the 0-ring 40b is between the ports 19 and 15, the 0-ring 40c is between the ports 15 and 22,
O-ring 40d is mounted between port 22 and the remainder of housing 25 and sleeve 37.

In this embodiment, the sleeve 37 is molded from polyesterimide resin, which has excellent stability and thermal insulation properties over a wide temperature range. A polyesterimide resin suitable for this purpose is General Electric Company (Ge
neral Electric Company) under the trademark rULTEMJ.

A spool 46 is disposed within the coaxial hole 38. The spool 46 has an elongated irregular shape, spans most of the bore 38 and has three interconnecting pistons 47.48.4.
Contains 9. Piston 47 is located at the left end of spool 46 and includes an annular Teflon seal member 47a sized to slide along the inner surface of bore 38 and a matching stainless steel spring member 47b.

The seal member 47a and the spring member 47b
6 and supports an annular flange 47c integrally formed with the annular flange 47c. This assembly is held in place by a threaded nut 47d.

The piston 48 also includes a Teflon sealing member 48a having a diameter that supports the cylindrical inner surface of the hole 38, and a stainless steel spring member 48b matching the shape of the sealing member 48a. Members 48a, 48b support a flange 48c integrally molded on the periphery, and the assembly is held in position by a split ring spring clamp 48d.

The piston 49 has a similar structure, and is comprised of a Teflon seal member 49a and a stainless steel spring member 49b of the same shape, and is held to the flange 49c by a rivet 49d.

It will be seen from the figure that the diameter of piston 47, 49 and associated bore 38 is of a first size, and the diameter of piston 48 and associated bore 38 is of a second size. The pistons 47, 48 are always in communication with the pressure of the input port 15 and have a predetermined effective surface area in combination. The effective surface area of the piston 49 is approximately twice the effective surface area of the combination of the pistons 47 and 48.

Spool 46 is slidable between a first position shown in FIG. 1 and a second position shown in FIG. In the second position, the refrigerant enters the port 15, exits the opening 41 through the annular recess 42, the opening 43, the opening 43 to the hole 38 between the pistons 47, 48, enters the annular recess 39, and enters the reversible It reaches flow port 19. At the same time, reversible flow port 2
A fluid path is formed that enters the recess 42 from 2 and reaches the coaxial hole 50 in the spool 46 and the output port 17 through the opening 45 .

When spool 46 is in the state of FIG. 2, a backflow cycle is established. Refrigerant from port 15 passes through annular recess 42 and opening 43 into bore 38 between pistons 47 , 48 and from there through opening 45 to annular recess 44 and reversible flow port 22 .

At the same time, the flow that has returned to the flow port 19 is transferred to the annular recess 3.
9, through opening 41 to hole 38, and then directly to port 1.
7 and is refluxed to the compressor 12.

Further referring to FIG. 1, a variable volume chamber 51 is formed at the right end of the hole 38 between the piston 49 and the right end of the sleeve 37. Right end of sleeve 37 and right housing part 2
A constant volume chamber 52 is formed between 7 and 7. Room 51.52
are interconnected by an opening 53.

An elongated bleed passage 54 is formed in sleeve member 37 and extends from annular recess 42 to chamber 52, a portion of which is shown in phantom. A filter screen 55 and an orifice member 56 are connected to the bleed passageway 54 upstream of the chamber 52.
is attached to.

A nozzle member 57 having a flow-restricting orifice is positioned to engage the right axial end of the sleeve 37 by the plunger 34. A bleed passage 58, shown in phantom in FIG. The pistons extend outwardly in the direction from which they extend longitudinally through the sleeve 37 and into communication with the bores 38 between the pistons 48,49. Since the sleeve 37 is integrally molded, the bleed passage 58 necessarily opens the sides and ends of the sleeve at the junction of its radial and axial sections. The side openings are sealed by O-rings 40e and the end openings are sealed by plugs 40f.

The 0-ring 40e and the plug 40f are the 0-ring 40a.
~40d also serves as a seal between the housing part 27 and the sleeve 37.

While the switching valve 11 is operating, the plunger 34 of the solenoid 33
is normally biased by a spring 35, and the solenoid 3
3 is in the position shown in FIG. 1 when in the de-energized state. In this position, plunger 34 engages nozzle 57 and seals bleed passage 58.

At the same time, refrigerant from compressor 12 enters input port 15 and annular recess 43 through conduit 16 . Some of this fluid enters the bleed passage 54 and enters the filter screen 5
5. reaches chamber 52 via orifice 56; Nozzle 5
7 is closed, all of the second fluid reaches chamber 51 through opening 53, and this pressure forces piston 49 to move to the leftmost position as shown in FIG.

The fluid entering the input port 15 and the annular recess 42 flows through the opening 4
3 also passes through the bore 38 between the pistons 47,48. Since piston 48 is larger than piston 47, the force created by this pressure differential moves the spool from left to right. However, since this force is weaker than the force exerted on piston 49 by the pressure within chamber 51, spool 46
It will be in the position shown in the figure. As mentioned above, when the switching valve 11 is in this position, compressed refrigerant entering the port 15 passes through the switching valve 11 and the outlet port 19 to the heat exchanger. The refrigerant returned from the heat exchanger 14 enters the inlet port 22, passes through the switching valve 11, and is discharged to the output port 17.
It is refluxed to the compressor 12.

In FIG. 2, an electrical signal is generated on low voltage line 36 to activate solenoid 33 when the preset temperature limit of the thermostat is reached. This retracts plunger 34 from engagement with nozzle 57, thus establishing communication between chamber 52 and bleed passage 58. The compressed refrigerant continues to move from input port 15 to chamber 52 via the bleed passage. However, since the nozzle 57 and the bleed passage 58 are open at this time, the chamber 52
The refrigerant therein flows out into the hole between the pistons 48, 49 and reaches the input or suction side of the compressor 12 via the coaxial hole 50 and the output 17. Chamber 52.51 is therefore under negative pressure. Since the pressurized refrigerant is always in communication via the input 15 and the opening 43 with the bore 38 between the pistons 47, 48,
The force generated by the differential pressure acting on these pistons moves spool 46 from left to right to the position shown in FIG. As mentioned above, the refrigerant thus compressed reaches the heat exchanger 14 from the manual power 15 via the switching valve 11 and the outflow port 22, and the refrigerant discharged from the heat exchanger 13 enters the port 19 and passes through the switching valve 11. It passes through the output port 17 and is returned to the compressor 12.

This condition continues as long as the thermostat is producing a signal on low voltage line 36. When the temperature limit previously set on the thermostat is again reached, the signal generated on the low voltage line 36 ceases and the solenoid plunger 34 returns to its normal extended position under the influence of the spring 35, as shown in FIG. Returning, the operating mode of the heat pump system changes as described above.

FIG. 3 shows another embodiment of the switching valve of the present invention, generally designated 61. Valve 61 is used in the same type of heat pump system with compressor 62 and heat exchanger 63,64. The input port 5 of the valve 61 is the compressor 62
is connected by a conduit 66 to the output of. The output port lower is connected to the input of compressor 62 by conduit 68.

Reversible port 69 is connected to heat exchanger 64 via conduit 71, while reversible port 72 is connected to heat exchanger 63 via conduit 73. These heat exchangers are interconnected by conduits 74, thereby completing the fluid loop.

Valve 61 includes a generally cylindrical housing 75 having a left side 76 and a right side 77. The diameter of the right side 77 is larger than the diameter of the left side. These parts have matching flanges 75a, 77a with an annular gasket inserted between them, and are hermetically connected by a plurality of screws 79.

The left housing portion 76 is closed at the left end, but an opening allo b for the input port 5 is formed on one side, and an opening allo C176d, 76e for the ports 67, 69, and 72 is formed on one side.
is provided on the opposite side of the opening arrow b.

The solenoid housing 81 has a cylindrical shape with one end closed and the other end open. The open end is stepped to fit and align with the closed end of the right housing portion 77, the two being secured in a manner similar to valve 11 as described below. More specifically, an open lower portion 7b is formed at the right end of the housing portion 77, and a thin stainless steel tube 90 with a flange formed at the left end surrounds the open lower portion 7b and protrudes coaxially to the right side of the housing. It is welded to the end of section 77. The solenoid 82 consists of an annular coil 82a with a hollow core and is supported by a tube 90. A movable core or plunger 83 is slidably disposed within tube 90 and opens lower opening 7.
It extends along b.

A compression spring 84 is provided between the fixed core 82b and the plunger 83, which normally urges the plunger 83 to the extended position shown in FIG. 4 in the de-energized state of the solenoid.

A threaded stud 82c secured to the closed end of tube 90 extends coaxially through the end of solenoid housing 81 and secures solenoid housing 81 to housing portion 77 by a nut 82d. With this structure, the solenoid and its related parts can be accessed by removing the nut 82d and housing 81.

When solenoid 82 is energized by a low voltage signal provided through a signal line from a thermostat (not shown), plunger 83 retracts to the position shown in FIG.

The left housing portion 76 is a plastic sleeve;
That is, it has a liner member 86. The liner member 86 is generally cylindrical and has a coaxial cylindrical hole 87 formed therein. Both ends of the sleeve 86 are open, and a radially projecting flange 88 is formed at the right end. The flange 88 coincides with and abuts against the end surface of the flange 76a. A first outer diameter of sleeve 86 corresponds to an inner diameter of left housing portion 76 . On the other hand, the outer diameter of the flange 88 corresponds to the inner diameter of the right housing portion 77 and is a precise fit.

A hole 91 extending in the radial direction is formed in the inner wall of the sleeve 86, and the input port 5 is joined to the hole 91, so that the port 65 and the coaxial hole 87 communicate with each other. On the opposite side of the sleeve 86 openings 92, 93, 94 are provided corresponding to the ports 67, 69, 72 and communicate these ports with the coaxial hole 87.

A plurality of annular grooves are formed at intervals in the liner 86,
O-rings 95a-95e are inserted here. All of these O-rings are connected to sleeve 86 and housing portion 76.
This is a sealing measure to prevent refrigerant leaks between the In particular, 0
- A ring 95a is arranged between the port 69 and the closed end of the housing part 76, sealingly separating the port 69 on the left side as shown in FIG. The 0-ring 95b is the third
As shown, ports 69 are hermetically separated on the right side. The O-ring 95c is attached diagonally and separates the port 65 in a sealed manner together with the O-ring 95b. 0
-Ring 95d is an O-ring 95 installed diagonally.
Separate port 67 with c. O-rings 95d and 95e hermetically separate ports 72.

A second plastic molded sleeve 96 of cylindrical shape is provided in housing portion 77 .

Sleeve 96 is open at both ends and includes an intermediate wall 97 , the left end of sleeve 96 abuts coaxially with the surface of flange 88 , while the right end of sleeve 96 abuts housing portion 77 .
coaxially abutted against the closed end of. Housing part 76.77 and sleeve 86.96 are screwed 79
are compressed by tightening and connected in a hermetically sealed manner. O-ring 100 prevents refrigerant from leaking between housing portion 77 and sleeve 96.

The intermediate wall 97 connects the hollow interior of the sleeve 96 to the variable volume chamber 9.
8 and a constant volume chamber 99. These functions will be described later.

Dual piston member 101 includes a first small annular piston 102 slidably disposed within bore 87 of sleeve 86 and a second large annular piston 103 slidably disposed within variable volume chamber 98. equip

The pistons 102, 103 each slide in a sealed manner within the chamber 87, 98, but neither piston crosses the joint of the plastic sleeve 86, 96. In this example, the effective area of piston 103 is twice that of piston 102 and therefore the force exerted by the fluid pressure is twice that of piston 102.

Dual piston member 101 includes an irregularly shaped member 103 molded from Teflon. The left end of member 103 partially forms piston 102, and the right end partially forms piston 103. The zero part 104, in which an annular groove 105 is formed between the pistons 102, 103 by the double piston part 101, is provided with a coaxial hole into which a plastic tubular part 106 is inserted. Tubular member 106 is provided with a chime portion 107 which is received within and forms a negative portion of small piston 102 . As shown in FIG. 3, a flat sliding member 10 projects coaxially from the flange 107 to the left and extends over a substantial portion of the sleeve 86. A rectangular opening 109 is formed in the sliding member 108 and holds the cup member 111. The cup member 111 has openings 92.94 or 92.94.
93 of sufficient longitudinal or axial dimension to selectively extend to 93. Another rectangular hole (not shown) is formed between the cup 111 of the sliding member 10B and the piston 102, through which the refrigerant passes. A Teflon lower surface 111a is formed on the bottom of cup 111 to ensure smooth sliding during operation. As evidenced by its convex or cup-like shape, the cup member 111 allows the refrigerant fluid to flow smoothly from one port to another.

In FIG. 5 of the cross-sectional view taken along cutting line 5--5 in FIG.
Sleeve 86 so that the upper part of 7 is annular and the side part is flat.
is molded. The lower part of the sleeve 86 is thicker and forms a flat surface 86a over which the lower surface 1
11a slides.

Still referring to FIG. 4, planar surface 86a terminates in an abutment surface 86b. Abutting surface 86b terminates the left piston 102. As shown in FIG. 4, the hole 87 has a circular cross section on the right side of the abutting surface 86b, and is adapted to receive the annular piston 102 therein.

Still referring to FIG. 5, the liner 86 is formed with a pair of diametrically opposed grooves 86c extending along the axis to slidably hold the sliding member 108.

Next, in FIG. 3, tubular member 106 has flange 107.
A rectangular block member 112 is provided between the sliding member 108 and the sliding member 108.
further including. The block member 112 comprises a small receptacle to which a filter screen 113 is attached. Screen 113 communicates with orifice passage 114, which in turn communicates with internal tubular bore 1 of tubular member 106.
It communicates with 15. The rightmost end of the tubular member 106 protrudes almost to the end of the right piston 103. This part is threaded and a large compression nut 116 is screwed into it. Nut 116 is aligned to coincide with the end of piston 103. Flange 107 and Teflon member 104
A stainless steel spring member 117 is inserted between the compression nut 116 and the Teflon member 104, and a similar spring member 118 is inserted between the compression nut 116 and the Teflon member 104. Spring elements 117, 118 serve to support the Teflon element 104 from behind in the region of the piston 102, 103.

Further in FIG.
8.99 to form a substantially unrestricted fluid communication path. An orifice passageway 122 is also formed in the axial center of wall 97 to provide a restricted fluid communication path between chambers 98,99. A resilient annular seal 123 is provided in wall 97 around orifice passage 122 in sealing engagement with the rightmost end of tubular member 106 (see FIG. 4).

On the opposite side of wall 97, orifice passage 122 terminates in a raised nozzle 124. The fulcrum lever 125 is attached to the wall 97
It includes a first closing pad 125a and a second closing pad 125b which are pivotally supported by and capable of sealing the orifice 122.

A compression spring 126 urges the fulcrum lever 125 to the position normally shown in FIG. That is, the closing pad 125a is not closed and the orifice passage 122 is open.

Closing pad 125b covers nozzle 127. Nozzle 127 is the output of a bleed passage 128 that extends radially outwardly within wall 97. The bleed passage 128 is a passage 128a and a passage 128.
It is divided into b. Passage 128 a extends radially inwardly and communicates with annular space 105 . On the other hand, passage 128
b extends longitudinally through the sleeve 86 to reach the connecting leg 128C. Connecting leg 128C extends radially outwardly to spacing opening 92 and port 67.

Port 67 is connected to the input of compressor 62 so that the entire passageway 128 and various passageways 128a-c are continuously exposed to suction pressure. As mentioned above, the fulcrum lever 125
is normally pressed to the position shown in FIG. 3 by spring 126, so that nozzle 127
occluded by

Next, the operation will be explained with reference to FIG. Compressed refrigerant is continuously supplied to hole 87 through port 65 and opening 91 . Due to the pressure of this refrigerant, the left piston 102
, a force is generated depending on the effective surface area. When dual piston member 101 is in the position shown in FIG. 3, it is introduced into variable volume chamber 98 through compressed filter screen 113, passageway 114 and tubular bore 115. Assuming that the pressure of the refrigerant in bore 87 and chamber 98 is the same, this pressure produces a second force on piston 103 that is twice as large as the force acting on piston 102. Therefore, the double piston member 101 moves from right to left and comes to the position shown in FIG.

At the same time, the compressed refrigerant moves through the openings 121;
Bring chamber 99 to the same pressure.

Solenoid 82 is shown in an energized state, such that plunger 83 is retracted as shown in FIG. Therefore, the plunger 83 is not in contact with the fulcrum lever 125 and the compression spring 126 presses the lever 125 to the position shown in FIG. engage in the same manner. When the nozzle 127 closes, the bleat passage 1
28 is the suction pressure inside the port 67. This suction pressure is created by connecting port 67 to the input of compressor 62. At this time, passage 128 is connected to chamber 99 or 98.
Since the passage 128 and the suction pressure do not affect the internal operation of the valve 61, the refrigerant pressure created at the output of the compressor 62 is therefore present in the bore 87 and the chamber 98, and the piston The force exerted on the left side by the difference in areas 102 and 103 causes the double piston member 101 to remain in the position shown in FIG.

, with the double piston member 101 in the position shown, the compressed refrigerant enters the input port 5 and enters the opening 9.
1 to hole 87 and from there through a rectangular opening (not shown) in sliding member 10 to opening 93 and reversible flow port 72.

From port 72, the refrigerant first enters heat exchanger 63, then through heat exchanger 64, and then through reversible flow port 69, opening 9.
4. Reverse the cup 111, the opening 92, the reflux port 67, and enter the input of the compressor 62.

When the temperature controlled by the thermostat reaches a predetermined limit, the thermostat changes its mode of operation and the signal on low voltage line 85 stops.

In this case, the solenoid 82 is not energized and the compression spring 84 presses the plunger 83 into engagement with the fulcrum lever 125, causing the butt 125a to move toward the nozzle 124.
and engage in a sealing manner. At the same time, the pad 125b is moved away from the nozzle 127, so it passes! A communication path between 12B and chamber 99 is opened.

Consequently, the pressure in chamber 99 and therefore in chamber 98 is
begins to decrease, and therefore the force acting on the piston 102 also begins to decrease. However, the pressure acting on the piston 102 does not change because it is connected to the output of the compressor 62. When the forces acting on piston 103 are sufficiently reduced, the forces on piston 102 take effect and double piston member 102 moves from the position shown in FIG. 3 to the position shown in FIG. 4. In this position, the cup member is at port 67.
．． Fluid is communicated between 72 to switch the operating cycle.

In the position shown in FIG. 4, the rightmost end of the tube member 106 has landed on the sealant 123 and the refrigerant is no longer flowing from the tube member 106 into the chamber 98.
Negative pressure in the passageway 128, which cannot flow into the chamber 99, is therefore present in the chamber 99 and the double piston member 1
01 is held in the position shown. At the same time, since the refrigerant is maintained by the sealant 123, the bleed passage 12
There is no way to drain the refrigerant.

When the diverter valve 61 is in the position shown in FIG.
and further reaches a heat exchanger 64. After refluxing through the heat exchanger 63, the refrigerant enters the reversible flow port 72, passes through the cup 111, enters the reflux port 67, and enters the compressor 62.
re-enter.

When the cycle switches again due to a change in the electrical signal on low voltage line 85, solenoid plunger 83 is energized and retracted. This allows the solenoid plunge +8
3 is removed from the fulcrum lever 124, and as a result, the nozzle 12
4 is opened and the nozzle 127 is closed. As a result,
Since the pressure in chamber 99 no longer escapes through passage 128 and passage 122 is open, the compressed refrigerant flows into passage 1.
22 into chamber 99 and further through opening 121 into chamber 98 . The pressure in these chambers therefore begins to increase, and at a critical point the force developed on the large piston 103 overcomes the force acting on the piston 102, causing the double piston member 101 to move from right to left and switch motion.

[Brief explanation of the drawing]

Figure 1 is included in the diagram representing the heat pump system, and the first
2 is a sectional view similar to FIG. 1 showing the switching valve in a second operating mode;
FIG. 3 shows a schematic diagram of a heat pump system.
FIG. 4 is a longitudinal section showing another embodiment of the heat pump switching valve in a second operating mode; FIG. 4 is a sectional view similar to FIG. 3, showing the switching valve in a second operating mode; is a cross-sectional view taken along line 5--5 of FIG. 4; 11., ,Switching valve, 12.,,Compressor, 13.14. ,,Heat exchanger 15, ,Input port, 17, ,Output port, 19.22. , Reversible flow port, 25, Housing, 33, Solenoid, 36, Low voltage line, 37, Sleeve, 46, Spool, 47, Piston. Patent applicant Yamatake Honeywell Co., Ltd. Agent Patent attorney Yoshiharu Matsushita

Claims (2)

[Claims] (1) A switching valve used in a heat pump system, etc., which has an input port, a reflux port, and first and second reversible valve ports, and has a valve body exterior of a predetermined length and a valve body exterior that is approximately the same as the valve body exterior. a sleeve member having a length, arranged to match the valve body exterior, having an opening formed in a transverse direction with an internal longitudinal hole, and communicating between each of the ports and the hole. movably disposed between a valve body and first and second positions within the bore, the first position providing fluid communication between the input port and one reversible flow port; Valve means for communicating fluid between the input port and the other reversible flow port and between the reflux port and the one reversible flow port, and continuously supplying fluid between the input port and the first and second pressure chambers. means for communicating with the first and second pressure chambers; control means for removing pressure from the second pressure chamber and reducing the pressure in the second pressure chamber in response to a predetermined control signal; a second pressure chamber is formed therein, and the valve means is moved to the first position when the first and second pressure chambers are at substantially the same pressure; differential pressure effecting means configured to move the valve means to the second position when reduced by the control means; (2) A switching valve used in a heat pump system, etc., comprising: a valve body having an input port, a reflux port, and first and second reversible valve ports; and between the first and second positions within the valve body. movably arranged, in the first position, fluid is communicated between the input port and the one reversible flow port, and in the second position, the input port and the other reversible flow port, and the reflux port and the one reversible flow port are in fluid communication. a valve means for communicating fluid with the port; first and second pressure chamber means formed within the valve body; and means for communicating fluid between the input port and the first and second pressure chambers. a first control means for releasing pressure from the second pressure chamber means and reducing the pressure in response to a predetermined control signal; second control means for ceasing removal of pressure from said second pressure chamber means in the presence of a control signal, when said first and second pressure chambers are at substantially the same pressure; a differential pressure action configured to move said valve means to said first position and move said valve means to said second position when pressure within said second pressure chamber is reduced by said control means; A switching valve consisting of means and.