WO2018090916A1

WO2018090916A1 - Bidirectional thermostatic expansion valve and system including same

Info

Publication number: WO2018090916A1
Application number: PCT/CN2017/110977
Authority: WO
Inventors: 韩荣耀
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2016-11-16
Filing date: 2017-11-15
Publication date: 2018-05-24

Abstract

Disclosed is a bidirectional thermostatic expansion valve, comprising a valve body (110), a valve core (130, 230), and a unidirectional flow assembly (150, 250). The valve body (110) comprises a valve seat (113), a first port (111) and a second port (112). The valve core (130, 230) is accommodated in the valve body (110) and has an abutting portion (133, 233) forming an orifice (120) with the valve seat (113), and the valve core (130, 230) can move relative to the valve body (110) between a first position and a second position. In the first position, the abutting portion (133, 233) abuts against the valve seat (113) so as to close the orifice (120); and in the second position, the abutting portion (133, 233) faces away from the valve seat (113) so as to open the orifice (120). The unidirectional flow assembly (150, 250) provides a flow path for communicating the first port (111) and the second port (112) and is constructed to allow a fluid to flow from the first port (111) to the second port (112) and prevent the fluid from flowing to the first port (111) from the second port (112).

Description

Bidirectional thermal expansion valve and system including the bidirectional thermal expansion valve

The present disclosure claims the priority of the Chinese Patent Application, filed on Nov. 16, 2016, the disclosure of which is hereby incorporated by reference.

Technical field

The present disclosure relates to a two-way thermal expansion valve.

Background technique

The content of this section merely provides background information related to the present disclosure, which may not constitute prior art.

The thermal expansion valve is a key component of the superheat of the control system in the refrigeration system and is typically installed between the condenser and the evaporator. The thermal expansion valve achieves a pressure drop from the condensing pressure to the evaporating pressure and regulates the flow of the refrigerant, thus directly determining the operating performance of the entire system.

The temperature sensing package is generally installed between the liquid storage cylinder (gas liquid separator) and the evaporator. The thermal expansion valve senses the outlet temperature of the evaporator through the temperature sensing package, thereby adjusting the opening degree of the throttle opening, that is, adjusting the mass flow rate of the refrigerant flowing into the evaporator, thereby adjusting the evaporator outlet temperature to ensure the superheat degree of the refrigerant. Stabilize and ensure that the gaseous refrigerant flows into the compressor to achieve safe operation of the compressor under reasonable evaporation efficiency.

A known two-way thermal expansion valve includes a valve body and a spool. A first port and a second port are disposed on the valve body. The bidirectional thermal expansion valve allows the refrigerant to flow along a first direction from the first port to the second port (which may be referred to as "forward flow") and along a second direction from the second port to the first port (may Called "reverse flow"). The spool is housed within the valve body and is moveable relative to the closed position of the valve body that closes the expansion valve against the valve seat on the valve body and the open position that opens the expansion valve away from the valve seat.

A throttle is formed between the spool and the valve body. The opening of the orifice can be adjusted by the evaporator outlet temperature sensed by the temperature sensing pack, thereby adjusting the mass flow rate of the refrigerant flowing through the orifice.

Generally, the forward flow of the refrigerant is different from the reverse flow of the refrigerant. For example, in a forward flow condition, the pressure difference between the first port and the second port is small, while in the reverse flow The pressure difference between the first port and the second port is larger under working conditions. In this example, in the case where the opening degree of the orifice is constant, for example, when the orifice is at the rated opening degree or the maximum opening degree, the flow rate of the refrigerant flowing through the orifice in the forward flow condition is higher. Small and thus its mass flow is small; while the flow rate of refrigerant flowing through the orifice under reverse flow conditions is large and thus its mass flow is large. In short, the greater the difference between the forward flow condition and the reverse flow condition, the greater the difference in refrigerant flow through the orifice. If the flow rate of the refrigerant flowing through the orifice is too small, the refrigeration capacity of the compressor will be lowered, and even the refrigeration requirement may not be met. On the other hand, if the flow rate of the refrigerant flowing through the orifice is too large, the refrigerant may not be sufficiently evaporated in the evaporator, causing the liquid refrigerant to enter the compressor and causing a liquid blow phenomenon, reducing the efficiency of the compressor, and even damaging the compression. mechanism.

Accordingly, it is desirable in the art to provide a two-way thermal expansion valve that is capable of meeting refrigerant flow requirements under both forward flow conditions and reverse flow conditions.

Summary of the invention

It is an object of the present disclosure to provide a two-way thermal expansion valve optimized for two-way operation (forward flow operation and reverse flow operation).

Another object of the present disclosure is to provide a two-way thermal expansion valve that is structurally simplified and/or less costly.

In accordance with an aspect of the present disclosure, a bidirectional thermal expansion valve is provided that includes a valve body, a spool, and a one-way flow assembly. The valve body has a valve seat, a first port, and a second port. The valve core is received in the valve body and has an abutting portion forming a throttle opening with the valve seat, and the valve core is movable relative to the valve body between the first position and the second position. In the first position, the abutting portion abuts The valve seat closes the throttle port; in the second position, the abutment portion is away from the valve seat to open the throttle port. The one-way flow assembly provides a flow path that communicates the first port and the second port and is configured to allow fluid to flow from the first port to the second port and to prevent fluid flow from the second port to the first port.

For the two-way thermal expansion valve of the present disclosure, the quality of the working fluid (eg, refrigerant) under forward flow conditions or reverse flow conditions can be changed by the one-way flow assembly due to the provision of the one-way flow assembly. flow. In this way, the structure and size of the unidirectional flow assembly can be designed according to the difference between the forward flow condition and the reverse flow condition, so that the bidirectional thermal expansion valve equipped with the one-way flow assembly can satisfactorily satisfy the forward flow. Demand for working conditions and reverse flow conditions. In addition, the one-way flow assembly can be designed according to the specific structure of the two-way thermal expansion valve, so only minor modifications to the existing thermal expansion valve are required, thereby greatly Reduce manufacturing costs and assembly costs.

Optionally, the one-way flow assembly includes a flow passage forming the flow path and is disposed in the flow passage to allow fluid to flow through the flow in a direction from the first port to the second port One-way valve for the passage.

Optionally, the flow passage includes a passage formed in the spool. For example, the flow passage includes a passage disposed in the abutment of the spool. The passages in the abutment are generally shorter in length. In this way, the processing difficulty can be reduced, and the stroke of the working fluid can be shortened to reduce the wear.

Optionally, the one-way valve is positioned adjacent to the passage in the spool.

Optionally, the one-way valve is a separate component and is secured to the end of the spool. In this way, the design of the check valve is flexible and easy to assemble and disassemble.

Optionally, the one-way valve includes a body defining a communication passage and a valve member, the communication passage communicating with the passage in the spool and defining a valve seat of the one-way valve, the valve member being capable of abutting The communication passage is closed or opened by the valve seat or spaced apart from the valve seat.

Optionally, the one-way valve further includes an end cap that retains the valve member within the body.

Optionally, a biasing member is disposed between the valve member and the end cap, the biasing member biasing the valve member toward a position to close the one-way valve. Optionally, the valve member is a spherical member, a tapered member, an arc-shaped member or an annular member.

Optionally, the one-way valve is integrally formed in the flow path, and a portion of the passage in the spool constitutes a valve seat of the one-way valve, and a valve member can abut the valve seat Or spaced apart from the valve seat to close or open the communication passage. With this configuration, the structure of the bidirectional thermal expansion valve of the present disclosure can be simplified and made compact.

Optionally, the one-way valve further includes an end cap that retains the valve member within the valve seat, the valve member being a spherical member, a tapered member, an arcuate member, or an annular member.

Optionally, the one-way valve includes a reed for opening and closing the flow passage.

Optionally, the flow passages are formed in a material that constitutes the valve body. Optionally, the flow passage is formed outside the valve body, and the one-way valve is disposed outside or inside the valve body.

In another aspect of the present disclosure, a system including the above described two-way thermal expansion valve is provided.

DRAWINGS

The features and advantages of one or more embodiments of the present disclosure will become more readily understood from

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic illustration of the refrigeration of a system employing a two-way thermal expansion valve.

Figure 2 is a schematic illustration of the heating conditions of a system employing a two-way thermal expansion valve.

3 is a schematic diagram of an example of the operation of the system of FIG. 1 under refrigeration conditions.

4 is a schematic illustration of an example of the operation of the system of FIG. 2 under heating conditions.

FIG. 5 is a longitudinal cross-sectional view of a bidirectional thermal expansion valve according to a first embodiment of the present disclosure.

Figure 6 is a cross-sectional view of the valve body of the bidirectional thermal expansion valve shown in Figure 5 .

Figure 7 is a cross-sectional view of the one-way flow assembly of the two-way thermal expansion valve shown in Figure 5.

Figure 8 is a cross-sectional view of the body of the one-way flow assembly shown in Figure 7.

Figure 9 is a cross-sectional view of the end cap of the one-way flow assembly of Figure 7.

10 is a longitudinal cross-sectional view of a bidirectional thermal expansion valve in accordance with a second embodiment of the present disclosure.

Figure 11 is a cross-sectional view of the spool and one-way flow assembly of Figure 10.

12 is a schematic diagram showing fluid flow of a two-way thermal expansion valve according to the present disclosure under refrigeration conditions.

13 is a schematic view showing fluid flow of a two-way thermal expansion valve according to the present disclosure under heating conditions.

detailed description

The following description of the preferred embodiments is merely exemplary and is not a limitation of the disclosure

The directions of "upper", "lower", "top", "bottom" and the like mentioned in the following description are only relative to the orientation of the thermal expansion valve shown in the drawing, and are capable of expanding the valve with the thermal force. Change in actual direction.

A system employing a two-way thermal expansion valve and its operating principle will be described below with reference to FIGS. 1 and 2.

The system 10 shown in FIGS. 1 and 2 includes a compressor 11, a four-way switching valve 12, a first heat exchanger (outdoor unit) 13, a two-way heat expansion valve 14, and a second heat exchanger (indoor unit) 15. A filter 18 may be disposed between the first heat exchanger 13 and the bidirectional thermal expansion valve 14. A liquid storage tank (gas liquid separator) 16 may be disposed between the four-way switching valve 12 and the compressor 11 upstream of the compressor 11.

In the first heat exchanger 13 as an evaporator (heating mode, as shown in Figure 2) or the second heat exchanger 15 (in cooling mode, as in Figure 1) with the reservoir 16 or the compressor 11 (without liquid storage) In the case of a can), a temperature sensing package 17 may be provided. The temperature sensing package 17 is for sensing the temperature of the fluid (refrigerant) coming out of the evaporator (the first heat exchanger 13 or the second heat exchanger 15) to determine the superheat of the fluid, thereby passing the heat through the tube 172. The expansion valve provides the corresponding pressure. Also. The balance tube 174 directs the refrigerant within the system 10 to the balance port of the bi-directional thermal expansion valve 14. The position of the spool of the bidirectional thermal expansion valve relative to the valve body is controlled according to the difference between the pressure provided by the tube 172 and the refrigerant pressure introduced through the balance tube 174, that is, the abutment portion of the control spool and the valve body The opening of the orifice between the seats. The degree of superheat of the refrigerant from the evaporator is maintained within a predetermined range by controlling the opening of the orifice of the bidirectional thermal expansion valve.

1 is a schematic illustration of a refrigeration condition of a system 10 employing a two-way thermal expansion valve. In the cooling condition, as shown in FIG. 1, the compressor 11 discharges a high-temperature high-pressure gaseous refrigerant (working medium), and the refrigerant enters the first heat exchanger 13 after passing through the four-way switching valve 12. The first heat exchanger 13 functions as a condenser under a cooling condition, and transfers heat of the refrigerant to the surrounding environment to obtain a liquid low-temperature high-pressure refrigerant. Subsequently, the refrigerant flows into the bidirectional thermal expansion valve 14 via the filter 18, and expands through the orifice thereof to become a low-temperature low-pressure mist refrigerant. The mist-like refrigerant discharged from the two-way heat expansion valve 14 flows into the second heat exchanger 15. The second heat exchanger 15 functions as an evaporator under refrigeration conditions, and the refrigerant absorbs heat in the evaporator to become gaseous to enter the compressor 11 for recycling. In this process, the thermal expansion valve 14 senses the temperature (i.e., superheat degree) of the refrigerant discharged from the second heat exchanger 15 as the evaporator, based on the temperature sensing package 17, and adjusts the thermal expansion based on the temperature. The opening of the valve 14.

2 is a schematic illustration of the heating conditions of system 10 employing a two-way thermal expansion valve. Pass Switching the four-way reversing valve 12 can cause the system 10 to transition from the refrigerating condition shown in Figure 1 to the heating condition shown in Figure 2. In the heating condition, as shown in FIG. 2, the compressor 11 discharges a high-temperature high-pressure gas refrigerant (working medium), and the refrigerant enters the second heat exchanger 15 after passing through the four-way switching valve 12. The second heat exchanger 15 functions as a condenser under heating conditions to transfer heat of the refrigerant to the surrounding environment, thereby heating the surrounding environment. Subsequently, the refrigerant flows into the bidirectional thermal expansion valve 14, and after its throttle opening, it expands into a low temperature and low pressure mist refrigerant. The mist-like refrigerant discharged from the two-way heat expansion valve 14 flows into the first heat exchanger 13 via the filter 18. The first heat exchanger 13 functions as an evaporator under heating conditions, and the refrigerant absorbs heat in the evaporator to become gaseous to enter the compressor 11 for recycling. In this process, the thermal expansion valve 14 senses the temperature (i.e., superheat degree) of the refrigerant discharged from the first heat exchanger 13 as the evaporator based on the temperature sensing package 17, and adjusts the thermal expansion based on the temperature. The opening of the valve 14.

As can be seen by reference to the description of Figures 1 and 2, the system 10 can achieve both refrigeration and heating by means of the four-way reversing valve 12 and the bi-directional thermal expansion valve 14. The refrigerant flows through the orifice of the bidirectional thermal expansion valve 14 in the opposite direction under both the cooling and heating conditions. The rated opening or the maximum opening of the throttle of the two-way thermal expansion valve 14 is the same under the cooling condition and the heating condition.

Generally, the difference between the cooling and heating conditions of the system is large. In the case where the opening of the orifice of the two-way thermal expansion valve is constant (for example, at the rated opening or the maximum opening), the mass flow of the refrigerant flowing through the orifice of the two-way thermal expansion valve is in the cooling Working conditions are significantly different from heating conditions. In the design of the system, typically the capacity of the thermal expansion valve is designed or selected to be optimal relative to the capacity of the condenser and evaporator under refrigeration conditions. However, under heating conditions, the above design may result in poor matching of the capacity of the thermal expansion valve with the capacity of the condenser and the evaporator, resulting in a decrease in efficiency or an increase in energy consumption of the entire system.

The differences between the two operating conditions of the system are described below by way of example with reference to Figures 3 and 4.

3 is a schematic diagram of an example of the operation of the system of FIG. 1 under refrigeration conditions. The two-way thermal expansion valve 14 has a first port 141 in fluid communication with the first heat exchanger 13 and a second port 142 in fluid communication with the second heat exchanger 15. In the cooling operation shown in FIG. 3, the refrigerant flows from the first port 141 to the second port 142 via the orifice. The first heat exchanger 13 serves as a condenser on the outdoor side, and the second heat exchanger 15 serves as an evaporator on the indoor side. It is assumed that the first heat exchanger 13 has a condensation temperature T1 of 50 ° C and a condensation pressure P1 of 267 psig; the second heat exchanger 15 has an evaporation temperature T2 of 10 ° C and an evaporation pressure P2 of 84 psig, and the difference between the condensation pressure and the evaporation pressure The value ΔP1 = P1 - P2 = 183 psig.

4 is a schematic illustration of an example of the operation of the system of FIG. 2 under heating conditions. In the heating operation shown in FIG. 4, the refrigerant flows from the second port 142 to the first port 141 via the orifice. The first heat exchanger 13 serves as an evaporator on the outdoor side, and the second heat exchanger 15 serves as a condenser on the indoor side. It is assumed that the second heat exchanger 15 has a condensation temperature T3 of 60 ° C and a condensation pressure P3 of 337 psig; the first heat exchanger 13 has an evaporation temperature T4 of -10 ° C and an evaporation pressure P4 of 37 psig, and the condensation pressure and the evaporation pressure The difference ΔP2 = P3 - P4 = 300 psig.

The differential pressure ΔP2 under heating conditions is significantly greater than the differential pressure ΔP1 under refrigeration conditions. In the case where the opening degree of the throttle opening of the two-way thermal expansion valve 14 is constant, since the pressure difference ΔP2 is significantly larger than the pressure difference ΔP1, the mass flow rate of the refrigerant under the heating condition is significantly larger than that in the cooling condition. The mass flow rate of the agent. The greater the difference between the two operating conditions, the greater the difference in the mass flow rate of the refrigerant.

The inventors have found the above problems and have proposed the present invention based on the above problems. A bidirectional thermal expansion valve according to the present disclosure will be described below with reference to FIGS. 5 to 13.

FIG. 5 is a longitudinal cross-sectional view of the bidirectional thermal expansion valve 100 according to the first embodiment of the present disclosure. As shown in FIG. 5, the bidirectional thermal expansion valve 100 includes a valve body (valve case) 110 and a valve body 130 housed in the valve body 110. The valve body 110 has a valve seat 113, and the valve body 130 has an abutment portion 133 that abuts or is away from the valve seat 113. The spool 130 is movable relative to the valve body 110 between a first position of the abutment portion 133 against the valve seat 113 and a second position of the abutment portion 133 away from the valve seat 113. An orifice 120 is formed between the abutting portion 133 and the valve seat 113. The abutting portion 133 closes the orifice 120 when abutting against the valve seat 113 to prevent the refrigerant from flowing through the orifice 120. The abutting portion 133 opens the orifice 120 when it is away from the valve seat 113 to allow the refrigerant to flow through the orifice 120.

The valve body 110 is further provided with a first port 111 and a second port 112 respectively located at two sides of the throttle port 120. In conjunction with the system illustrated in FIG. 1, the first port 111 can be in fluid communication with the first heat exchanger 13 and the second port 112 can be in fluid communication with the second heat exchanger 15. Under refrigeration conditions, refrigerant flows from the first port 111 through the orifice 120 to the second port 112 (which may be referred to as "forward flow"). Under heating conditions, refrigerant flows from the second port 112 via the orifice 120 to the first port 111 (which may be referred to as "reverse flow").

The bidirectional thermal expansion valve 100 in accordance with the present disclosure also includes a one-way flow assembly 150. The one-way flow assembly 150 is configured to allow refrigerant from one of the first port 111 and the second port 112 The person flows to the other but prevents the refrigerant from flowing from the other of the first port 111 and the second port 112 to the one. In short, the one-way flow assembly 150 allows refrigerant to flow in only one direction between the first port 111 and the second port 112.

As shown in the example of FIG. 5, the one-way flow assembly 150 is configured to allow refrigerant to flow from the first port 111 to the second port 112 but prevents refrigerant from flowing from the second port 112 to the first port 111. As such, in the cooling condition, while the refrigerant flowing into the first port 111 flows to the second port 112 via the orifice 120, the refrigerant may also pass from the first port through the additional flow path provided by the one-way flow assembly 150. 111 flows to the second port 112, as shown in Figure 12, thereby providing a larger flow cross section. In the heating condition, the refrigerant flowing into the second port 112 flows only to the first port 111 through the orifice 120, and cannot flow to the first port 111 through the unidirectional flow assembly 150 (at this time, by the one-way flow) The additional flow path provided by assembly 150 is closed, as shown in Figure 13, thereby providing a smaller flow cross section.

Compared with the existing two-way thermal expansion valve without the one-way flow assembly, the two-way thermal expansion valve 100 shown in FIG. 5 has the mass flow rate of the refrigerant passing through the two-way thermal expansion valve under the cooling condition due to the one-way flow assembly 150. The capacity is greatly increased, whereby the cooling capacity (refrigeration capacity) and the cooling efficiency of the system including the two-way thermal expansion valve can be improved. Thus, when the capacity of the thermal expansion valve is designed or selected to optimize the capacity of the condenser and the evaporator under refrigeration conditions (in this case, the differential pressure experienced by the thermal expansion valve) Smaller, but providing a larger flow cross-section to provide a predetermined overall cooling capacity. Under heating conditions, the capacity of the thermal expansion valve can also be better matched to the capacity of the condenser and evaporator (at this time) The thermal expansion valve is subjected to a large differential pressure, but provides a smaller flow cross-section that generally provides the desired amount of refrigeration. In addition, by designing the cross-sectional area of the additional flow path provided by the one-way flow assembly 150, both the heating and cooling conditions in which the system is located can be optimized simultaneously to obtain optimal conditions under both operating conditions. System efficiency. In particular, in addition, by designing the cross-sectional area of the additional flow path provided by the one-way flow assembly 150, the system can be easily adapted to a climatic environment such as the South or North and achieve good system efficiency.

The additional flow path provided by the one-way flow assembly can be formed in the valve body (valve housing) and/or outside the valve body (valve housing). For example, the one-way flow assembly can include a conduit that fluidly connects the first port to the second port, which can be located entirely outside the valve body (ie, the entire flow path is outside the valve body), or can be completely within the valve body (ie, the entire body) The flow path is in the valve body), or one part may be outside the valve body and the other part may be located in the valve body (ie, The entire flow path includes a portion outside the valve body and a portion within the valve body).

The one-way flow assembly includes a flow passage that forms a flow path and a one-way valve disposed in the flow path to allow fluid to flow through the flow passage in a direction from the first port to the second port. The flow passage may include a passage formed in one or more components (eg, a valve body or a spool) of the thermal expansion valve. The one-way valve may be a separate piece and connected in the flow path, or the one-way valve may be integrally formed in the flow path.

An example of the bidirectional thermal expansion valve according to the present disclosure will be described in detail below with reference to the accompanying drawings. It should be understood that the two-way thermal expansion valve of the present disclosure is not limited to the illustrated examples, and the illustrated examples are for illustrative purposes only.

5 to 9 illustrate a bidirectional thermal expansion valve 100 and components thereof according to a first embodiment of the present disclosure. As shown in FIG. 5, the one-way flow assembly 150 includes a passage 134 disposed in the abutment portion 133 of the spool 130 and a one-way valve 152 adjacent the passage 134. The one-way valve 152 includes a body 151 and a valve member 152a disposed in the body 151. A valve seat 152b is defined on the main body 151. The valve member 152a is movable between a closed position against the valve seat 152b to close the passage 134 and an open position away from the valve seat 152b to open the passage 134.

A one-way valve 152 is installed at an end of the spool 130 adjacent to the second port 112 (lower end portion as shown in FIG. 6) 135. The one-way valve 152 includes a recess 155 that receives the end 135 of the spool 130 (shown in Figures 7 and 8). The end 135 of the spool 130 can be interference fit in the recess 155 of the one-way flow assembly 150, thereby securing the one-way flow assembly 150 to the spool 130. As shown in Figure 6. After the one-way valve 152 is assembled to the spool 130, the one-way valve 152 directly abuts against the abutment portion 133 of the spool 130, and the communication passage 154 of the one-way valve 152 is aligned with the passage 134 of the abutment portion 133 and Connected. As such, the first port 111 is in fluid communication with the second port 112 via the passage 134 and the communication passage 154.

In the illustrated example, the one-way valve 152 is configured to allow refrigerant to flow from the first port 111 to the second port 112 but prevents refrigerant from flowing from the second port 112 to the first port 111. The check valve 152 is located on the downstream side of the communication passage 154 in the forward flow direction (flow direction from the first port 111 to the second port 112).

Although the one-way valve 152 is installed at the lower end portion 135 of the spool 130 in the illustrated example, the one-way valve 152 may be installed at any suitable position as long as the one-way valve 152 can perform the above functions. For example, the one-way valve 152 may be installed outside the valve body 110, or may be installed in the valve body 110, or may be mounted on the valve core other than the lower end portion thereof. At his location, this depends on the setting of the flow path provided by the one-way flow assembly 150.

In the illustrated example, the valve member 152a has a circular cross section and is received in the body 151 of the one-way flow assembly 150. Accordingly, the housing 151 of the one-way flow assembly 150 is provided with a receiving portion 157 for accommodating the valve member 152a. In the illustrated example, the receiving portion 157 has a tapered cross section. The valve seat 152b may be formed on the accommodating portion 157, may be formed on the transition portion of the accommodating portion 157 and the communication passage 154, or may be formed on the end portion of the communication passage 154.

In the cooling condition, the one-way valve 152 is in an open state, and the refrigerant from the first port 111 flows through the passage 134 and the communication passage 154 and flows through the one-way valve 152 to the second port 112. Under heating conditions, the high pressure of the refrigerant from the second port 12 acts on the valve member 152a of the one-way valve 152, moving the valve member 152a toward the communication passage 154 to abut the valve seat 152b to close the communication passage 154, And the refrigerant is prevented from flowing from the second port 112 to the first port 111 via the passage 134.

The communication passage 154 may be in the form of a circular hole, an arcuate groove or a circular groove. Accordingly, the valve member 152a can be a spherical member (as shown), a tapered member, an arcuate member, or a toroidal member. In addition, the number, shape structure, relative position, and the like of the communication passage 154 and the check valve 152 may be changed according to actual needs. In other examples, the one-way valve may be a reed at the end of the flow channel or may be any other member capable of performing the functions described above.

The one-way flow assembly 150 can also include an end cap 156. The end cap 156 is located on the underside of the one-way valve 152. Valve member 152a can be moved between end cap 156 and communication passage 154. The end cap 156 can be configured to prevent the valve member 152a from falling and allowing refrigerant to flow out of the one-way flow assembly 150 when the one-way valve 152 is open. The end cap 156 can include a recess 159 that receives the boss 153 of the body 151. The boss 153 can be fit fit in the recess 159.

In other examples, the end cap may have a recess for directly receiving the lower end 135 of the spool 130. The lower end portion 135 of the spool 130 may be interference fit in the recess, thereby clamping the body of the one-way flow assembly between the end cap and the abutment. In such an example, the boss 153 of the body 151 of the one-way flow assembly 150 can be omitted. The position, structure or size of the end cap can be changed according to actual needs.

Alternatively, the main body 151 and the end cap 156 of the one-way flow assembly 150 may be provided with through

holes

158a and 158b for introducing refrigerant located on the second port 112 side to the upper portion of the spool to achieve pressure balance. The structure of each component of the one-way flow assembly 150 can be based on the valve body and The structure of the spool changes and changes.

In other examples, the one-way flow assembly can include a biasing member that biases the valve member of the one-way valve toward the flow passage. The biasing member can be disposed between the valve member and the end cap. The biasing member can be a compression spring.

FIG. 10 is a longitudinal cross-sectional view of a bidirectional thermal expansion valve 200 in accordance with a second embodiment of the present disclosure. Figure 11 is a cross-sectional view of the spool and one-way flow assembly of Figure 10. The bidirectional thermal expansion valve of the second embodiment is different from the bidirectional thermal expansion valve of the first embodiment only in that the main body of the check valve and the valve body are integrally formed in the second embodiment.

As shown in FIGS. 10 and 11, the abutment portion 233 of the bidirectional thermal expansion valve 200 also serves as the main body of the one-way flow assembly 250. A passage 234 is provided in the abutting portion 233. A valve member 252a of the check valve 252 is provided on the lower side of the passage 234. In this example, the passage 234 is equivalent to the passage 134 and the communication passage 154 in the example shown in FIG. A portion of the passage 234 in the spool may constitute the valve seat 252b of the one-way valve. The valve member 252a can be spaced against or spaced from the valve seat 252b to close or open the passage (or communication passage). An end cap 256 is provided on the underside of the one-way valve 252 with an interference fit with the lower end of the spool (or in any other suitable manner, such as threaded, riveted, bonded, welded, snapped, etc.).

Although the various embodiments of the present disclosure have been described in detail herein, it is understood that the invention is not limited to The skilled person implements other variations and variants. All such variations and modifications are intended to fall within the scope of the present disclosure. Moreover, all of the components described herein can be replaced by other technically equivalent components.

Claims

A two-way thermal expansion valve comprising:

a valve body (110) having a valve seat (113), a first port (111) and a second port (112);

a spool (130, 230), the spool (130, 230) being received in the valve body (110) and having an abutment portion forming a throttle (120) with the valve seat (113) ( 133, 233), the valve core (130, 230) is movable relative to the valve body (110) between a first position and a second position, in the first position, the abutment (133) , 233) abutting the valve seat (113) to close the throttle port (120); in the second position, the abutting portion (133, 233) is away from the valve seat (113) to open The throttle port (120);

a one-way flow assembly (150, 250) that provides a flow path connecting the first port (111) and the second port (112) and configured to allow fluid to pass from The first port (111) flows to the second port (112) and prevents fluid from flowing from the second port (112) to the first port (111).
The bidirectional thermal expansion valve according to claim 1, wherein said one-way flow assembly (150, 250) includes a flow passage forming said flow path and disposed in said flow passage to allow fluid to follow A check valve (152, 252) flowing through the flow passage in a direction from the first port (111) to the second port (112).
The two-way thermal expansion valve according to claim 2, wherein the flow passage includes a passage formed in the spool (130, 230).
The two-way thermal expansion valve according to claim 2, wherein the flow passage includes a passage (134, 234) provided in the abutment (133) of the spool.
The two-way thermal expansion valve of claim 4 wherein said one-way valve (152, 252) is positioned adjacent said passage (134, 234) in said spool.
The two-way thermal expansion valve according to claim 5, wherein the one-way valve (152) is a separate component and is fixed to an end of the spool.
The two-way thermal expansion valve according to claim 5, wherein said one-way valve (152) includes a body (151) defining a communication passage (154) and a valve member (152a), said communication passage (154) a communication with the passage (134) in the spool and defining a valve seat (152b) of the one-way valve, the valve member (152a) being able to abut the valve seat (152b) or with the valve seat (152b) spaced apart to close or open the communication passage (154).
The two-way thermal expansion valve of claim 7 wherein said one-way valve (152) further comprises an end cap (156) that retains said valve member (152a) within body (151).
The bidirectional thermal expansion valve according to claim 8, wherein a biasing member is provided between the valve member (152a) and the end cap (156), and the biasing member places the valve member (152a) is biased toward a position at which the one-way valve is closed.
The bidirectional thermal expansion valve according to claim 8, wherein the valve member (152a) is a spherical member, a tapered member, an arcuate member, or an annular member.
The bidirectional thermal expansion valve according to claim 5, wherein said one-way valve (252) is integrally formed in said flow path, and a part of said passage (234) in said spool is constituted The valve seat (252b) of the one-way valve, the valve member (252a) can be spaced against or spaced apart from the valve seat (252b) to close or open the communication passage (154).
The bidirectional thermal expansion valve of claim 11 wherein said one-way valve (252) further comprises an end cap (256) for retaining said valve member (252a) within said valve seat (252b) The valve member (252a) is a spherical member, a tapered member, an arcuate member, or an annular member.
A bidirectional thermal expansion valve according to any one of claims 2 to 6, characterized in that The check valve includes a reed for opening and closing the flow passage.
The bidirectional thermal expansion valve according to claim 2, wherein said flow passage is formed in a material constituting said valve body (110).
The bidirectional thermal expansion valve according to claim 2, wherein said flow passage is formed outside said valve body (110), and said one-way valve is disposed outside or inside said valve body.
A system comprising a bidirectional thermal expansion valve according to any one of claims 1 to 15.