CN210196498U

CN210196498U - Throttle valve and air conditioner

Info

Publication number: CN210196498U
Application number: CN201921027783.7U
Authority: CN
Inventors: Zhenkun Xu; 徐振坤; Zhisheng Cai; 蔡志昇; Shunkai Du; 杜顺开
Original assignee: Midea Group Co Ltd; Wuhu Meizhi Air Conditioning Equipment Co Ltd
Current assignee: Midea Group Co Ltd; Wuhu Meizhi Air Conditioning Equipment Co Ltd
Priority date: 2019-07-03
Filing date: 2019-07-03
Publication date: 2020-03-27
Anticipated expiration: 2029-07-03

Abstract

The utility model provides a choke valve and air conditioner, the choke valve includes: a valve body; a valve seat provided with a throttle hole; the valve needle is positioned in the throttling hole; the driving device drives the valve seat to move relative to the valve needle; the valve needle comprises a throttling part which comprises a first valve needle section and a second valve needle section, the change rate of the area of the through-flow gap between the first valve needle section and the throttling hole is different from the change rate of the area of the through-flow gap between the second valve needle section and the throttling hole, the driving device can drive the throttling hole to move relative to the throttling part, and the change rate of the area of the through-flow gap is different from the change rate of the area of the through-flow gap between the second valve needle section. The utility model provides a choke valve is through setting up the needle of the different many valve needle section types of multistage and orifice circulation clearance area, and only need install a choke valve on the air conditioner, alright in order to make the air conditioner work under multiple special scene to solve the high load, the low-load, frosting leaks the scheduling problem, need not additionally set up the bypass increase cost simultaneously, also need not directly shut down and influence the travelling comfort effect.

Description

Throttle valve and air conditioner

Technical Field

The utility model relates to a refrigeration plant field, more specifically relates to a choke valve and air conditioner including this choke valve.

Background

The air conditioner can often meet a plurality of special scenes such as high load, low load, frosting, leakage and the like when running in certain indoor and outdoor temperature and humidity and installation environments, and the solution is also various, for example, when the air conditioner is at high temperature and high pressure, bypass unloading or direct frequency reduction shutdown is adopted; or when the load is low during refrigeration, the temperature can not be maintained and is not reduced when the lowest operable frequency is reduced, and the machine needs to be stopped; or when the leakage and the exhaust of the refrigerant are high, the frequency is reduced or the machine is stopped to ensure the reliability preferentially, and the like.

Although these methods can solve the above problems, they have many disadvantages, such as increased cost due to the bypass unloading, reduced production and manufacturing efficiency, and direct shutdown to affect comfort.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least.

To this end, an aspect of the present invention is to provide a throttle valve.

Another aspect of the present invention is to provide an air conditioner including the above throttle valve.

In order to achieve the above object, an aspect of the present invention provides a throttle valve, including: the valve body is provided with a first inlet and a second inlet which are communicated with the valve cavity; the valve seat is positioned in the valve cavity, and an orifice is arranged on the valve seat; the valve needle is positioned in the throttling hole; the driving device is connected with the valve seat so as to drive the valve seat to move relative to the valve needle; the valve needle comprises a throttle portion comprising a first needle section and a second needle section, the throttle portion being locatable within the throttle bore, the first inlet/outlet and the second inlet/outlet communicate with each other through a flow gap between the throttle portion and the throttle hole in a direction from the first needle section to the second needle section, the rate of change of the area S1 of the flow gap between the first needle section and the orifice differs from the rate of change of the area S2 of the flow gap between the second needle section and the orifice, the driving device drives the throttle hole to move relative to the throttle part so as to change the change rate of the area of the through-flow gap between the throttle part and the throttle hole, wherein the first valve needle section and the second valve needle section are arranged in sequence along a direction of movement of the valve needle relative to the valve seat.

The utility model provides a throttle valve, through setting up throttle portion and the orifice that can move about from top to bottom, work as throttle portion for during the orifice up-and-down motion, clearance constantly changes between throttle portion and the orifice to the realization is to the regulation of flow. The regulating valve is applied to an air conditioner, and the flow of the condensing agent can be controlled through the regulating valve so as to realize the regulation of the condensing agent. Of course, the method can also be applied to other devices to realize the flow control function of the device. It is worth mentioning that when the flow rate of the throttle valve needs to be adjusted, the driving device drives the valve seat to move up and down, so that the throttle hole moves up and down relative to the throttle part, and relative to the technical scheme that the valve seat fixes the valve needle to move up and down, the cross-sectional area of the valve seat is larger than that of the valve needle, when the first inlet and the second inlet are not in throttling conduction, the flow rate passing through the first inlet and the second inlet in unit time with large cross-sectional area is larger, and for the air conditioner, the air conditioner can play a role in more rapidly eliminating or relieving abnormal phenomena such as high temperature and high pressure, frosting, leakage and the. In addition, the periphery of the valve seat is abutted against the inner wall of the valve cavity, and the valve seat is more stable than the valve needle in the process of up-and-down movement. Further, the throttling part is a first valve needle section and a second valve needle section connected with the first valve needle section in a turning mode, and the change rates of the cross sections of the first valve needle section and the second valve needle section are different. The valve needle segment with the large change rate of the cross section is short in length, rapid adjustment of flow can be achieved, the valve needle segment with the small change rate of the cross section is long in length, accurate adjustment of flow can be achieved, and the change of flow is stable in the valve seat moving process.

Therefore, the utility model provides a throttle valve passes through the orifice for throttle portion moves, adjusts the aperture of throttle valve, and then gets rid of or alleviates above-mentioned abnormal phenomenon, can also further adjust the condensing agent velocity of flow through the aperture that corresponds two stages of first valve needle section and second valve needle section (correspond valve seat position 0 to valve seat position 1 and valve seat position 1 to valve seat position 2 respectively) difference, with further getting rid of or alleviating above-mentioned abnormal phenomenon, thereby can satisfy the different refrigeration of air conditioner and the many use scene demands that heat respectively. On the other hand, compared with the related art solution, there is no need to separately provide a bypass for performing the unloading operation, and thus the manufacturing cost is not increased, and on the other hand, compared with the related art solution, there is no need to perform the shutdown operation, and thus the normal use of the user is not affected. Meanwhile, as can be understood by those skilled in the art, when the valve seat is moved to a position where the valve needle is located above the second inlet/outlet (from the valve seat position 0 to the valve seat position 3), the pressure can be quickly unloaded by the refrigerant bypass without throttling, instead of the bypass valve, and the equipment cost can be correspondingly reduced. Thus, the utility model provides a choke valve is through setting up the needle of the different many valve needle section types of multistage and orifice circulation clearance area, and only need install a choke valve on the air conditioner, alright in order to make the air conditioner work under multiple special scene to solve high load, the low-load, frosting leaks the scheduling problem, need not additionally set up the bypass increase cost simultaneously, also need not directly shut down and influence the travelling comfort effect.

Additionally, the utility model discloses above-mentioned technical scheme provides a choke valve still has following additional technical characteristic:

in one embodiment, the driving device drives the valve needle to move relative to the valve seat along the axial direction of the valve needle, the valve needle includes a connecting portion, the connecting portion and the throttling portion are sequentially arranged along the axial direction of the valve needle, the connecting portion is connected to the valve body, the second valve needle section is arranged between the first valve needle section and the connecting portion, and the variation rate of the area S1 of the through-flow gap between the first valve needle section and the throttling hole is greater than the variation rate of the area S2 of the through-flow gap between the second valve needle section and the throttling hole.

The flow curve of choke valve is along with the aperture is linear variation, the cross-sectional area of needle from the top down diminishes, follows needle from the top down is connecting portion, second valve needle section and first valve needle section in proper order, connecting portion are cylindricly, and its one end is connected in the top of valve body, and the other end is connected second valve needle section, first valve needle section is close to first access & exit one side, second valve needle section is close to second access & exit one side. When the valve seat moves from the first inlet and outlet side to the second inlet and outlet side (from the valve seat position 0 to the valve seat position 1), the throttling action is gradually reduced, the slope change of the needle section of the second valve is not large, and the throttling action is still obvious when the throttling valve is fully opened, so that the throttling valve cannot be used as a full-open valve, and under certain conditions, the switching between large flow and proper flow required by refrigeration or defrosting is not met, and the possibility or the time spent on failing to eliminate or relieve abnormal phenomena such as high temperature and high pressure, frosting, leakage and the like is long, so that the use comfort is influenced. In this way, when the valve seat moves from the second valve needle section to the first valve needle section (i.e. from the valve seat position 1 to the valve seat position 2), the gap between the orifice and the valve needle is suddenly increased, so that the flow rate is suddenly increased, which is beneficial to reducing or eliminating the throttling function of the expansion valve in the fully open state, and further eliminating or relieving abnormal phenomena such as high temperature and high pressure, frosting, leakage and the like. The throttle valve is used for improving the service performance of the air conditioner by providing refrigerants with different flow rates under different conditions, for example, the air conditioner is usually automatically protected and stopped due to overpressure when the air conditioner is at high temperature and high pressure, and the throttle valve is used by providing refrigerants with proper flow rates, so that the service performance of the air conditioner is improved, and the comfort effect is improved.

In one embodiment, the cross-sectional area of the first valve needle section gradually increases in a direction from the first valve needle section to the second valve needle section, and the area S1 of the through-flow gap between the first valve needle section and the orifice gradually decreases so that the rate of change of the area S1 of the through-flow gap is constant.

By setting the shape of the first valve needle section, the change rate of the same flow area S1 is the same, so that the change rate of the refrigerant flow corresponding to the same flow area S1 is constant, that is, when the first valve needle section is located in the throttle hole and moves relative to the throttle hole under the driving of the driving device, the change rate of the refrigerant flow is constant, so that the refrigerant can smoothly and stably flow through the area S1 of the through-flow gap between the first valve needle section and the throttle hole.

In one embodiment, the cross-sectional area of the second valve needle section gradually increases in a direction from the first valve needle section to the second valve needle section, and the area S2 of the through-flow gap between the second valve needle section and the orifice gradually decreases, so that the rate of change of the area S2 of the through-flow gap is constant.

By setting the shape of the second valve needle section, the change rate of the same flow area S2 is the same, so that the change rate of the refrigerant flow corresponding to the same flow area S2 is constant, that is, when the second valve needle section is located in the orifice and moves relative to the orifice under the driving of the driving device, the change rate of the refrigerant flow is constant, so that the refrigerant can smoothly and stably flow through the area S2 of the through-flow gap between the second valve needle section and the orifice.

In one embodiment, the area S1 of the flow gap between the first needle segment and the orifice is greater than the area S2 of the flow gap between the second needle segment and the orifice in the direction from the first needle segment to the second needle segment.

The driving device sequentially drives the second valve needle section to be located in the throttling hole, the second valve needle section to be separated from the throttling hole, the first valve needle section to be located in the throttling hole and the first valve needle section to be separated from the throttling hole, the refrigerant flow is always increased, and the change rate of the refrigerant flow is also increased, so that the refrigerant flow can be increased at a smaller first rate when the air conditioner is abnormal, and the refrigerant flow can be increased at a larger second rate when the abnormal condition cannot be solved.

When the connection of the first valve needle section and the second valve needle section is located in the throttle bore, the flow area changes abruptly, a transition is made between the rate of change of the area S1 of the flow passage gap and the rate of change of the common flow area S2, i.e. between the first rate and the second rate.

When the connection of the first valve needle section and the second valve needle section is located in the throttle bore, the flow area changes abruptly, a transition is made between the rate of change of the area S1 of the flow gap and the rate of change of the area S2 of the flow gap, i.e. between the first rate V1 and the second rate V2.

In one embodiment, the outer wall surface of the first valve needle section is in a convex cambered surface shape or a conical shape.

The convex arc surface shape or the conical shape is simple to process, and the change rate of the area S1 of the through-flow gap is the same from the first valve needle section to the second valve needle section, so that the flow rate of the refrigerant is stably increased.

It will be appreciated that the outer wall surface of the first valve pin section may be other than convex or conical.

In one embodiment, the outer wall surface of the second valve needle section is in a convex arc shape or a circular truncated cone shape.

The convex arc surface shape or the circular truncated cone shape is easy to process, and the change rate of the area S1 of the through-flow gap is the same from the first valve needle section to the second valve needle section, so that the flow rate of the refrigerant is stably increased.

It will be appreciated that the outer wall of the second valve needle section may be other than convex arcuate or frusto-conical.

In one embodiment, the maximum area of the through-flow gap between the first valve needle section and the throttle hole is S1max, and the maximum area of the through-flow gap between the second valve needle section and the throttle hole is S2max, so that S1max/S2max is 2 ≤ and 10 ≤.

When the second valve needle section is positioned in the throttling hole, the refrigerant flow is increased according to a first rate, when the first valve needle section is controlled to be positioned in the throttling hole, the refrigerant flow is increased according to a second rate, S1max/S2max is more than or equal to 2 and less than or equal to 10, so that the difference value between S1max and S2max is kept in a proper range, and thus, the difference value between the first rate and the second rate is in a proper range, and when the problem that the problem of the abnormality of the air conditioner cannot be solved due to the fact that the refrigerant flow is increased at the first rate, the problem that the abnormality of the air conditioner can be solved due to the fact that the refrigerant flow. S1max/S2max may be 2, 4, 6, 8, or 10. Further, 2 is less than or equal to S1max/S2max is less than or equal to 5.

The maximum value of the refrigerant flow rate corresponding to the area S1max of the maximum through flow gap between the first valve needle section and the throttle hole is Q2, and the maximum value of the refrigerant flow rate corresponding to the area S2max of the maximum through flow gap between the second valve needle section and the throttle hole is Q1, so that the ratio of Q2/Q1 is more than or equal to 2 and less than or equal to 10. Q2/Q1 can be 2, 4, 6, 8 or 10. Furthermore, Q2/Q1 is more than or equal to 2 and less than or equal to 5.

In one embodiment, the flow rate of the throttle valve corresponding to the maximum area S1max of the through-flow gap between the first valve needle section and the throttle hole is Q2, the flow rate of the throttle valve corresponding to the minimum area S2min of the through-flow gap between the second valve needle section and the throttle hole is Q0, 0.1Mpa air is introduced into the throttle valve, 0L/min is not less than Q0 and not more than 8L/min, the rated refrigerating capacity of the air conditioner is less than 4500W, 10L/min is not less than Q2 and not more than 80L/min, the rated refrigerating capacity of the air conditioner is in the range of 4500W-14000W, and 20L/min is not less than Q2 and not more than 150L/min.

The normal operation of the air conditioner can be ensured by limiting the upper limit value Q2 of the flow of the refrigerant at the second speed, and the requirement for solving the abnormal operation of the air conditioner can be met by limiting the upper limit value Q2 (target flow) under the premise that the flow of the refrigerant is less than or equal to the target flow under the normal condition, wherein the target flow is determined according to the rated heat exchange quantity of the air conditioner, so that the normal operation of indoor cooling or heating is ensured while the problem of the abnormal operation of the air conditioner is solved, and the comfort degree of using the air conditioner by a user can be further ensured.

The different air conditioner models have different heat exchange capacities, and the heat exchange capacity can be represented by a rated heat exchange amount, for example, the air conditioner is 35, and the rated cooling capacity of the air conditioner is 3500W, which can also be referred to as 1.5 HP.

Specifically, in the refrigeration mode, the rated heat exchange amount is the rated refrigeration amount, for example, the rated refrigeration amount is 4500W or lower than 4500W, the corresponding target flow rate is 10L/min ≤ Q2 ≤ 80L/min, and if the rated refrigeration amount is 4500W to 14000W, the corresponding target flow rate is 20L/min ≤ Q2 ≤ 150L/min.

The throttle valve is communicated with a valve cavity, the air flow rate is detected under 0.1MPa, air under 0.1MPa enters the valve cavity from the first inlet and the first outlet and flows out from the second inlet and the second outlet through the throttle hole, and the technical conditions are met: q0 is more than or equal to 0L/min and less than or equal to 8L/min.

The ranges and comparison values of the flow parameters Q2 and Q0 are median (not including the upper and lower deviations), namely Q2 is more than or equal to 10L/min and less than or equal to 80L/min, Q2 is more than or equal to 20L/min and less than or equal to 150L/min, and Q2 and Q0 are average values in Q0 is more than or equal to 0L/min and less than or equal to 8L/min.

Q0 and Q2 were measured with 0.1MPa of air introduced into the throttle. The rated refrigerating capacity of the air conditioner is less than 4500W, Q2 is more than or equal to 10L/min and less than or equal to 80L/min, and Q2 can be 10L/min, 50L/min or 80L/min. The rated refrigerating capacity of the air conditioner is 4500-14000W, Q2 is more than or equal to 20L/min and less than or equal to 150L/min, and Q2 can be 20L/min, 100L/min or 150L/min. Q0 is not less than 0L/min and not more than 8L/min, and Q0 can be 0L/min, 4L/min or 8L/min.

In one embodiment, the flow rate of the throttle valve corresponding to the maximum area S1max of the through-flow gap between the first valve needle section and the throttle hole is Q2, the flow rate of the throttle valve corresponding to the maximum area S2max of the through-flow gap between the second valve needle section and the throttle hole is Q1, the flow rate of the throttle valve corresponding to the minimum area S2min of the through-flow gap between the second valve needle section and the throttle hole is Q0, the opening of the throttle valve corresponding to Q2 is exv2, the opening of the throttle valve corresponding to Q1 is exv1, the opening of the throttle valve corresponding to Q0 is exv0, then 150 steps are not less than exv1 and not more than 400 steps, 50 steps are not less than exv2-exv1 and not more than 350 steps, and 0 step not less than exv0 and not more than 100 steps.

By controlling the opening of the throttle valve within a certain range, the requirements on Q0, Q1 and Q2 are met, on one hand, the abnormal phenomena of the air conditioner can be eliminated or relieved by adjusting the throttle valve within the range of exv0, exv1 and exv2, and on the other hand, the negative influence on the performance of the air conditioner caused by the excessively large increase of the opening of the throttle valve is also prevented.

150 steps is not less than exv1 and not more than 400 steps, exv1 can be 150 steps, 300 steps or 400 steps, 50 steps is not less than exv2-exv1 and not more than 350 steps, exv2-exv1 can be 50 steps, 200 steps or 350 steps, 0 step is not less than exv0 and not more than 100 steps, and exv2-exv0 can be 0 step, 50 steps or 100 steps.

In any of the above solutions, the extreme position of the valve seat with respect to the movement of the valve needle is located on a side of the second inlet/outlet port facing away from the first inlet/outlet port.

The limit position (valve seat position 3) is located on one side, away from the first inlet and outlet, of the second inlet and outlet and corresponds to the reverse conduction opening exv3, when the valve seat moves to the valve seat position 3, the valve seat continues to move upwards, namely the valve seat is not conducted through an orifice, at the moment, the flow area is greatly changed, the valve seat is similar to a refrigerant bypass and is not throttled, the pressure can be quickly unloaded, the function of a bypass valve is replaced, and the equipment cost can be correspondingly reduced.

In one embodiment, in the limit position, the maximum flow through the throttle is Q3, the maximum flow between the second needle section and the throttle bore is Q1, and Q3/Q1 is 5 or more.

The maximum flow rate Q3 through the throttle valve corresponds to a state in which the valve seat is moved to the limit position, the first inlet/outlet and the second inlet/outlet communicate with each other through the valve chamber without passing through the orifice, and Q1 corresponds to a refrigerant flow rate corresponding to the area S2max of the maximum flow gap between the second valve needle section and the orifice. The ratio of Q3/Q1 is set, and the values of Q3/Q2 and Q2/Q1 can be indirectly adjusted, so that the abnormal condition of the air conditioner can be solved according to the control method in the application.

In one embodiment, in the limit position, the opening degree of the throttle valve is exv3, and 50 steps are less than or equal to 0-exv3 and less than or equal to 500 steps.

The flow rate is gradually increased by adjusting the flow rates from 0 to exv3 in the reverse direction, and the flow rate is instantly increased by changing the flow rates in steps before and after exv 3. When the valve seat moves to the valve seat position 3 and then continues to move upwards, the conduction without the throttling hole can be realized, at the moment, the flow area sharply changes, the flow area is similar to that of a refrigerant bypass without throttling, the pressure can be quickly unloaded, the effect of a bypass valve is replaced, and the equipment cost can be correspondingly reduced.

In one embodiment, the valve body comprises an outer layer and an inner layer which are spaced from each other, the inner layer defines the valve cavity, a bypass space is defined between the inner layer and the outer layer, a bypass hole is formed in the inner layer and is communicated with the bypass space and the valve cavity, and the first inlet and the first outlet penetrate through the inner layer and the outer layer and are communicated with the bypass space; the valve seat moves relative to the valve needle to open or close the bypass hole, wherein the valve needle is withdrawn from the orifice, and the valve seat opens the bypass hole.

The first inlet and outlet extends through the inner layer and through the outer layer such that the first inlet and outlet is in communication with the bypass space and with the valve chamber. When the valve seat opens the bypass hole, the refrigerant flowing in from the first inlet and outlet can enter the valve cavity and flow into the second inlet and outlet, and the refrigerant flowing in from the first inlet and outlet can also enter the bypass hole from the bypass space and flow into the second inlet and outlet from the valve cavity. After the bypass hole is opened, the refrigerant can enter the valve cavity from the bypass hole, so that the inflow amount of the refrigerant in the valve cavity is increased, and the throttling effect can be weakened.

Furthermore, when the throttling part is separated from the throttling hole and the valve seat continues to move in the direction away from the valve needle after the throttling part is separated from the throttling hole, the valve seat opens the bypass hole, the flow area is changed sharply at the moment, the amount of the refrigerant flowing into the valve cavity is increased instantly, and the refrigerant bypass is similar to that of the refrigerant bypass without throttling.

In one embodiment, the valve seat opens the bypass hole, the maximum flow through the throttle valve is Q4, the maximum flow between the second valve needle section and the throttle hole is Q1, and Q4/Q1 is more than or equal to 5.

The maximum flow rate Q4 of the refrigerant flowing through the throttle valve corresponds to a state in which the throttle portion is disengaged from the orifice and the bypass hole is fully opened, and the state Q1 corresponds to a refrigerant flow rate corresponding to the maximum flow area S2max between the second needle section and the orifice. The ratio of Q4/Q1 is set, and the values of Q4/Q2 and Q2/Q1 can be indirectly adjusted, so that the abnormal condition of the air conditioner can be solved according to the control method in the application.

Furthermore, Q4/Q1 is more than or equal to 20 and less than or equal to 100.

In one embodiment, the valve seat opens the bypass hole, the opening degree of the throttle valve is exv4, the flow rate of the throttle valve corresponding to the maximum flow area S2max between the second valve needle section and the throttle hole is Q1, and the opening degree of the throttle valve corresponding to Q1 is exv1, and then 150 steps are not more than exv4 and exv1 steps are not more than 400 steps.

The range of exv4-exv1 is set so that the abnormal situation of the air conditioner can be solved according to the control method in the present application. exv4-exv1 can be 150 steps, 200 steps, 250 steps, 300 steps, 350 steps or 400 steps.

In any one of the above technical solutions, one of the first access opening and the second access opening is horizontally disposed, and the other is vertically disposed.

The first inlet and outlet is arranged at the bottom of the valve body and is arranged along the vertical direction, and the second inlet and outlet is arranged on the side wall of the valve body and is arranged along the horizontal direction. Control requirements for the interval exv 1-exv 2: when the excitation speed of the flow exv 1-exv 2 in the direction of the first port → the second port is equal to or less than 90pps, and when the excitation speed of the flow exv 1-exv 2 in the direction of the second port → the first port is equal to or more than 30pps, the flow in the direction of the second port → the first port is preferable.

In the case of a cooling and heating type air conditioner, when cooling and heating are simultaneously required, the heating preferably flows in the direction from the second inlet/outlet → the first inlet/outlet, that is, the second inlet/outlet is connected to the evaporator and the first inlet/outlet is connected to the condenser (although the first inlet/outlet is connected to the evaporator and the second inlet/outlet is connected to the condenser, it is necessary to control the excitation speed with care).

In any of the above technical solutions, the driving device includes a motor, the throttle valve includes a connecting rod, one end of the connecting rod is connected to a motor shaft of the motor, the other end of the connecting rod is connected to the valve seat, the valve body is connected to a sleeve, the connecting rod is located in the sleeve and is in threaded connection with the sleeve, the valve body is connected to a positioning member, the valve needle is connected to a sleeve, the sleeve is located in the positioning member and is in threaded connection with the positioning member, so that the motor drives the connecting rod and the valve seat to rotate to drive the valve seat to move relative to the valve needle; or the driving device comprises a motor, a gear is connected to a motor shaft of the motor, a rack is connected to the valve seat, and the gear is meshed with the rack so that the motor drives the valve seat to move relative to the valve needle.

And the coil and the magnet which are arranged outside the valve body are matched together to be equivalent to a motor to form a driving device of the valve seat. When the flow control of the throttling valve needs to be adjusted to change, a proper pulse signal is applied to the coil, the magnet is driven by the coil to rotate and drives the connecting rod to rotate together, the connecting rod and the sleeve sleeved on the outer side of the connecting rod form threaded fit, and the sleeve is fixed on the valve body, so that the connecting rod also axially moves up and down while rotating, and the valve seat is driven to move up and down, the throttling hole in the valve seat moves up and down relative to the throttling part, the flow of a refrigerant passing through the throttling hole is changed, and the flow control of a refrigeration system is realized. Or, be connected with the condition of setting element on the valve body, the sleeve cover is established in the outside of connecting rod, the sleeve be located the setting element and with setting element threaded connection, the motor drives the connecting rod motion, the connecting rod drives the sleeve motion, the sleeve rotates for the setting element to realize disk seat and sleeve along the axial motion of needle, under this kind of condition, can avoid setting up the intensity that the screw thread influences the needle on the needle, furtherly, the setting element is annular, annular internal face and sleeve threaded connection. The positioning piece and the sleeve are both positioned in the valve cavity.

The motor comprises a coil (stator) and a magnet (rotor) positioned on the inner side of the coil, the connecting part of the valve needle is connected with the magnet and positioned on the inner side of the magnet, and a spring is supported between the tail end of the connecting part and the magnet. Further, the motor is a stepping motor.

The motor can drive the valve seat to reciprocate up and down relative to the valve needle by driving the valve seat to rotate, and can also drive the valve seat to reciprocate up and down relative to the valve needle without rotating the connecting rod through the meshing of the gear and the rack.

The utility model discloses technical scheme of second aspect provides an air conditioner, include: a compressor having a discharge port and a return port; a four-way valve having a first port to a fourth port, one of the first port and the third port being communicated with the second port, the other of the first port and the third port being communicated with the fourth port, the first port being connected to the exhaust port, the third port being connected to the return air port; the second port is connected with the first end of the indoor heat exchanger, and the fourth port is connected with the first end of the outdoor heat exchanger; the throttling valve of any one of the aspects of the first aspect, the throttling valve being connected in series between the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger.

The utility model discloses the air conditioner that technical scheme of second aspect provided, because of including any one of the technical scheme of first aspect the choke valve, therefore have any one of them embodiment any one the whole beneficial effect of choke valve, no longer describe herein.

In one embodiment, an air conditioner includes: and the auxiliary heater is arranged close to the indoor heat exchanger and used for heating the indoor heat exchanger.

The indoor unit comprises an indoor heat exchanger and an indoor fan, and the indoor unit also comprises an auxiliary heater for starting auxiliary heating to the room when defrosting operation is carried out. For a cooling and heating machine type, when the indoor machine is provided with the auxiliary heater, the auxiliary heater can be forcibly electrified when heating and defrosting are carried out, so that the auxiliary heater works, and the effect of defrosting without reversing is improved.

Further, the auxiliary heater is located between the indoor fan and the indoor heat exchanger.

In one embodiment, one of the first inlet and the second inlet of the throttle valve, which is horizontally arranged, is connected with the indoor heat exchanger, and the other of the first inlet and the second inlet of the throttle valve, which is vertically arranged, is connected with the outdoor heat exchanger.

For example, when the first doorway is vertically arranged and the second doorway is horizontally arranged, the control requirements for the section exv1 to exv2 are as follows: when the excitation speed of the flow exv 1-exv 2 is equal to or less than 90pps in the direction of the flow → the second inlet/outlet, and when the excitation speed of the flow exv 1-exv 2 is equal to or more than 30pps in the direction of the flow → the first inlet/outlet. Therefore, in the cooling and heating type air conditioner, the refrigerant flow direction during heating is optionally from the second inlet/outlet to the first inlet/outlet. It is understood that the refrigerant flow direction during heating may also be from the first inlet/outlet to the second inlet/outlet, in which case, the first inlet/outlet is connected to the indoor heat exchanger, and the second inlet/outlet is connected to the outdoor heat exchanger, but it is necessary to control the excitation speed.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 is a schematic cross-sectional structural view of a throttle valve according to a first embodiment of the present invention;

fig. 2(a) to 2(c) are a front view and a top view of an assembly structure of a valve seat and a valve needle according to a first embodiment of the present invention, wherein a first valve needle section of the valve needle in fig. 2(a) is conical, a second valve needle section is truncated cone-shaped, a first valve needle section of the valve needle in fig. 2(b) is convex arc-shaped, a second valve needle section is truncated cone-shaped, a first valve needle section of the valve needle in fig. 2(c) is conical, and a second valve needle section is convex arc-shaped;

fig. 3 is a schematic view illustrating a relationship between an opening degree of a throttle valve and a refrigerant flow rate according to a first embodiment of the present invention;

fig. 4(a) and 4(b) are schematic structural diagrams of a throttle valve according to a first embodiment of the present invention, in which fig. 4(a) illustrates a refrigerant flowing in from a first inlet/outlet and flowing out from a second inlet/outlet, and fig. 4(b) illustrates a refrigerant flowing in from the second inlet/outlet and flowing out from the first inlet/outlet;

fig. 5 is a schematic structural diagram of an air conditioning system according to a first embodiment of the present invention;

fig. 6 is a schematic structural diagram of an air conditioning system according to a first embodiment of the present invention;

fig. 7 is a flowchart of a control method for solving the high-low pressure unloading according to a first embodiment of the present invention;

fig. 8 is a flowchart of a control method for solving the problem of excessive exhaust temperature (leakage and blockage) according to a first embodiment of the present invention;

fig. 9 is a flowchart of a control method for alleviating heating frosting according to a first embodiment of the present invention;

fig. 10 is a flowchart of a control method for solving heating defrosting according to a first embodiment of the present invention;

fig. 11 is a flowchart of a control method for solving the problem of low shutdown temperature fluctuation of the refrigeration load according to a first embodiment of the present invention;

fig. 12 is a schematic view illustrating a relationship between an opening degree of a throttle valve and a refrigerant flow rate according to a second embodiment of the present invention;

fig. 13 is a schematic view illustrating a relationship between an opening degree of a throttle valve and a refrigerant flow rate according to a second embodiment of the present invention;

fig. 14 is a flowchart of a control method for solving the high-low pressure unloading according to the second embodiment of the present invention;

fig. 15 is a flowchart of a control method for solving the problem of excessive exhaust temperature (leakage and blockage) according to the second embodiment of the present invention;

fig. 16 is a flowchart of a control method for alleviating heating frosting according to the second embodiment of the present invention;

fig. 17 is a flowchart of a control method for solving heating and defrosting according to a second embodiment of the present invention;

fig. 18 is a flowchart of a control method for solving the problem of low shutdown temperature fluctuation of the refrigeration load according to the second embodiment of the present invention.

Wherein, the correspondence between the reference numbers and the component names in fig. 1 to 18 is:

10 throttling valve, 11 spring, 12 motor, 121 coil, 122 magnet, 13 valve needle, 131 throttling part, 132 first valve needle section, 133 second valve needle section, 134 connecting part, 14 valve body, 141 sleeve, 142 positioning part, 143 valve cavity, 144 inner layer, 145 outer layer, 146 first inlet and outlet, 147 second inlet and outlet, 148 bypass space, 149 bypass hole, 15 valve seat, 151 throttling hole, 152 connecting rod, 21 compressor, 211 exhaust port, 212 return port, 22 four-way valve, 23 outdoor fan, 24 outdoor heat exchanger, 25 indoor fan, 26 indoor heat exchanger and 27 auxiliary heater.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention more clearly understood, the present invention will be described in further detail with reference to the accompanying drawings and detailed description. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

A throttle valve and an air conditioner according to some embodiments of the present invention will be described below with reference to fig. 1 to 18.

As shown in fig. 1, according to some embodiments of the present invention, there is provided a throttle valve 10, including: a valve body 14 defining a valve chamber 143, the valve body 14 being provided with a first inlet and outlet 146 and a second inlet and outlet 147 communicating with the valve chamber 143; the valve seat 15 is positioned in the valve cavity 143, and the throttling hole 151 is formed in the valve seat 15; a needle 13 located within the orifice 151; the driving device is connected with the valve seat 15 to drive the valve seat 15 to move relative to the valve needle 13; the needle 13 includes a throttle portion 131, the throttle portion 131 includes a first needle segment 132 and a second needle segment 133, the throttle portion 131 is located in the orifice 151, the first inlet and outlet 146 and the second inlet and outlet 147 communicate through a flow-through gap between the throttle portion 131 and the orifice 151, a rate of change of an area S1 of the flow-through gap between the first needle segment 132 and the orifice 151 is different from a rate of change of an area S2 of the flow-through gap between the second needle segment 133 and the orifice 151 in a direction from the first needle segment to the second needle segment, and the drive device moves the orifice 151 relative to the throttle portion 131 to change the rate of change of the area of the flow-through gap between the throttle portion 131 and the orifice 151, wherein the first needle segment 132 and the second needle segment 133 are sequentially arranged in a moving direction of the needle 13 relative to the valve seat 15.

The utility model provides a throttle valve 10, through setting up throttle portion 131 and the orifice 151 that can move about from top to bottom for the needle, when throttle portion 131 when moving about the orifice, the clearance between throttle portion 131 and the orifice 151 constantly changes to the realization is to the regulation of flow. The regulating valve is applied to an air conditioner, and the flow of the condensing agent can be controlled through the regulating valve so as to realize the regulation of the condensing agent. Of course, the method can also be applied to other devices to realize the flow control function of the device. It should be noted that when the flow rate of the throttle valve 10 needs to be adjusted, the valve seat 15 is driven by the driving device to move up and down, so that the orifice 151 moves up and down relative to the throttle portion 131, and in the embodiment where the valve needle 13 is fixed to the valve seat 15 to move up and down, the cross-sectional area of the valve seat 15 is larger than that of the valve needle 13, when the first inlet/outlet 146 and the second inlet/outlet 147 are not in throttling conduction, the flow rate passing through the first inlet/outlet and the second inlet/outlet in a unit time with a large cross-sectional area is larger, and for an air conditioner, the air conditioner can play a role in more rapidly eliminating or relieving abnormal phenomena such as high temperature. In addition, the valve seat 15 is abutted against the inner wall of the valve cavity 143 at the periphery, and is more stable than the valve needle 13 in the process of up-and-down movement. The throttle portion 131 is further divided into a first needle section 132 and a second needle section 133 connected to the first needle section 132 at turns, and the first needle section 132 and the second needle section 133 have different rates of change in cross section. The valve needle 13 with the large change rate of the cross section is short in length and can realize rapid adjustment of flow, the valve needle 13 with the small change rate of the cross section is long in length and can realize accurate adjustment of flow, and the change of the flow is more stable in the moving process of the valve seat 15.

Thus, the utility model provides a throttle valve 10 passes through orifice 151 for the motion of throttle portion 131, adjust throttle valve 10's aperture, and then get rid of or alleviate above-mentioned abnormal phenomenon, can also be through corresponding the different apertures in two stages (corresponding disk seat 15 position 0 to disk seat 15 position 1 and disk seat 15 position 1 to disk seat 15 position 2) of first valve needle section 132 and second valve needle section 133 respectively, further adjust the condensing agent velocity of flow, with further getting rid of or alleviating above-mentioned abnormal phenomenon, thereby can satisfy the different refrigeration of air conditioner and the many use scene demands of heating respectively. On the other hand, compared with the solutions of the related art, a bypass for executing the unloading operation is not required to be separately arranged, the system structure of the air conditioner is simplified, and a control component unit of the air conditioner is not additionally arranged, so that the preparation cost is not increased, the production efficiency is improved, and on the other hand, compared with the solutions of the related art, the shutdown operation is not required to be executed, so that the normal use of a user is not influenced. Meanwhile, as can be understood by those skilled in the art, when the valve seat 15 is moved to a position where the valve needle 13 is located above the second inlet/outlet 147 (from the position 0 of the valve seat 15 to the position 3 of the valve seat 15), the refrigerant bypass is not throttled, the pressure can be quickly unloaded, the function of the bypass valve is replaced, and the equipment cost can be correspondingly reduced.

The first embodiment is as follows:

the driving device drives the valve needle 13 to move relative to the valve seat 15 along the axial direction of the valve needle 13, the valve needle 13 comprises a connecting part 134, the connecting part 134 and the throttling part 131 are sequentially arranged along the axial direction of the valve needle 13, the connecting part 134 is connected to the valve body 14, the second valve needle section 133 is arranged between the first valve needle section 132 and the connecting part 134, and the change rate of the area S1 of the through-flow gap between the first valve needle section 132 and the throttling hole 151 is larger than the change rate of the area S2 of the through-flow gap between the second valve needle section 133 and the throttling hole 151.

The flow curve of the throttle valve 10 is linearly changed according to the opening degree, the cross-sectional area of the valve needle 13 from top to bottom is reduced, as shown in fig. 1, the first valve needle section 132, the second valve needle section 133 and the connecting portion 134 are sequentially arranged, the first valve needle section 132 may be a free end of the valve needle 13, the valve needle 13 moves in the axial direction (up-down direction) of the valve needle 13 relative to the valve seat 15, the connecting portion 134, the second valve needle section 133 and the first valve needle section 132 are sequentially arranged from top to bottom along the valve needle 13, the connecting portion 134 is cylindrical, one end of the connecting portion is connected to the top of the valve body 14, the other end of the connecting portion is connected to the second valve needle section 133, the first valve needle section 132 is close to the first inlet/outlet 146, the valve seat 15 is located at the bottom of the valve cavity. When the valve seat 15 moves from the second inlet/outlet 147 side to the first inlet/outlet 146 side (from the position 0 of the valve seat 15 to the position 1 of the valve seat 15), the throttling action is gradually reduced, the slope change of the second valve needle section 133 is not large, and the throttling action is still obvious when the throttle valve 10 is fully opened, so that the throttle valve 10 cannot be applied as a full-open valve, and in some cases, the switching between a large flow rate and a proper flow rate required when refrigeration or defrosting is required cannot be met, and the possibility or the time spent on failing to eliminate or relieve abnormal phenomena such as high temperature and high pressure, frosting, leakage and the like is long, thereby affecting the use comfort. In this way, when the valve seat 15 moves from the second valve needle section 133 to the first valve needle section 132 (i.e. from the position 1 of the valve seat 15 to the position 2 of the valve seat 15), the gap between the orifice 151 and the valve needle 13 increases abruptly, so that the flow rate increases abruptly, which is beneficial to reducing or eliminating the throttling function of the expansion valve in the fully open state, and further eliminating or relieving abnormal phenomena such as high temperature and high pressure, frost formation, leakage, and the like. The air conditioner is usually automatically protected to stop due to overpressure by providing refrigerants with different flow rates under different conditions, for example, when the air conditioner is at high temperature and high pressure, and the usability of the throttle valve 10 is provided through the refrigerants with proper flow rates, so that the usability of the air conditioner is improved, and the comfort effect is improved.

In the above embodiment, the cross-sectional area of the first needle section 132 gradually increases in the direction from the first needle section 132 to the second needle section 133 (in the direction from the position 2 of the valve seat 15 to the position 1 of the valve seat 15), and the area S1 of the through-flow gap between the first needle section 132 and the orifice 151 gradually decreases to make the rate of change of the area S1 of the through-flow gap constant.

By setting the shape of the first valve needle segment 132, the rate of change of the same flow area S1 is the same, so that the rate of change of the refrigerant flow rate corresponding to the same flow area S1 is constant, that is, when the first valve needle segment 132 is located in the orifice 151 and moves relative to the orifice 151 under the driving of the driving device, the rate of change of the refrigerant flow rate is constant, so that the refrigerant can smoothly and smoothly flow through the area S1 of the through-flow gap between the first valve needle segment 132 and the orifice 151.

In the above embodiment, the cross-sectional area of the second needle segment 133 gradually increases in the direction from the first needle segment 132 to the second needle segment 133 (in the direction from the position 1 of the valve seat 15 to the position 0 of the valve seat 15), and the area S2 of the through-flow gap between the second needle segment 133 and the orifice 151 gradually decreases to make the rate of change of the area S2 of the through-flow gap constant.

By setting the shape of the second valve needle segment 133, the rate of change of the same flow area S2 is the same, so that the rate of change of the refrigerant flow rate corresponding to the same flow area S2 is constant, that is, when the second valve needle segment 133 is located in the orifice 151 and moves relative to the orifice 151 under the driving of the driving device, the rate of change of the refrigerant flow rate is constant, and the refrigerant can smoothly and smoothly flow through the area S2 of the through-flow gap between the second valve needle segment 133 and the orifice 151.

In the above embodiment, the area S1 of the through-flow clearance between the first needle segment 132 and the orifice 151 is larger than the area S2 of the through-flow clearance between the second needle segment 133 and the orifice 151 in the direction from the first needle segment 132 to the second needle segment 133.

The driving device sequentially drives the second valve needle segment 133 to be positioned in the orifice 151, the second valve needle segment 133 to be disengaged from the orifice 151, the first valve needle segment 132 to be positioned in the orifice 151 and the first valve needle segment 132 to be disengaged from the orifice 151, the refrigerant flow rate is always increased, and the change rate of the refrigerant flow rate is also increased, so that the refrigerant flow rate can be increased at a first low rate when the air conditioner is abnormal, and the refrigerant flow rate can be increased at a second high rate when the abnormal condition cannot be solved.

The cross-sectional area at the junction of the first needle section 132 and the second needle section 133 is abrupt, and therefore, when the junction of the first needle section 132 and the second needle section 133 is located in the orifice 151, the flow area is abrupt, and a transition between the rate of change of the area S1 of the flow-through gap and the rate of change of the same flow area S2, i.e., a transition between the first rate and the second rate, is achieved.

When the connection of the first valve needle section 132 and the second valve needle section 133 is located in the throttle bore 151, the flow area changes abruptly, a transition is made between the rate of change of the area S1 of the flow passage gap and the rate of change of the area S2 of the flow passage gap, i.e. between the first rate V1 and the second rate V2.

In the above embodiment, the outer wall surface of the first valve pin section 132 has a convex arc shape or a conical shape.

The convex arc surface shape or the conical shape is processed simply, and the change rate of the area S1 of the through-flow gap is the same from the first valve needle section 132 to the second valve needle section 133, thereby realizing the smooth increase of the refrigerant flow.

As shown in fig. 2(a), the first valve needle section 132 of the valve needle 13 is conical, the second valve needle section 133 is circular truncated cone-shaped, the first valve needle section 132 of the valve needle 13 in fig. 2(b) is convex arc-shaped, the second valve needle section 133 is circular truncated cone-shaped, the first valve needle section 132 of the valve needle 13 in fig. 2(c) is conical, and the second valve needle section 133 is convex arc-shaped.

It will be appreciated that the outer wall surface of the first valve pin section 132 may be other than convex arcuate or conical.

In the above embodiment, the outer wall surface of the second valve needle section 133 has a convex arc shape or a truncated cone shape.

The convex arc surface shape or the circular truncated cone shape is easy to process, and the change rate of the area S1 of the through-flow gap from the first valve needle section 132 to the second valve needle section 133 can be the same, so that the flow rate of the refrigerant is stably increased.

It will be appreciated that the outer wall of the second valve needle section 133 may be other than convex arcuate or frusto-conical.

In the above-described embodiment, when the maximum area of the through-flow gap between the first needle segment 132 and the orifice 151 is S1max and the maximum area of the through-flow gap between the second needle segment 133 and the orifice 151 is S2max, S1max/S2max is 2 ≦ 10.

As shown in fig. 2(a), 2(b) and 2(c), S1max is S3+ S4, and S2max is S3. In the formula 3, exv1 corresponds to a flow area S3, exv2 corresponds to a flow area S3+ S4, (S3+ S4)/S3 ═ K1, and K1 has a value range of 2-10, preferably 2-5.

The flow area S3 is the area of the gap between the orifice 151 and the second needle segment 133 during the movement of the valve seat 15 from the position 0 of the valve seat 15 to the position 1 of the valve seat 15, and the flow area S3+ S4 is the area of the gap between the orifice 151 and the first needle segment 132 during the movement of the valve seat 15 from the position 1 of the valve seat 15 to the position 2 of the valve seat 15.

When the second valve needle section 133 is positioned in the orifice 151, the refrigerant flow rate is increased according to a first rate, when the first valve needle section 132 is controlled to be positioned in the orifice 151, the refrigerant flow rate is increased according to a second rate, and S1max/S2max are more than or equal to 2 and less than or equal to 10, so that the difference between S1max and S2max is kept in a proper range, and thus, the difference between the first rate and the second rate is in a proper range, when the problem of the air conditioner abnormality cannot be solved by increasing the refrigerant flow rate at the first rate, the problem of the air conditioner abnormality can be solved by increasing the refrigerant flow rate at the second rate at a high probability. S1max/S2max may be 2, 4, 6, 8, or 10. Further, 2 is less than or equal to S1max/S2max is less than or equal to 5.

As shown in fig. 3, the throttle valve 10 provided by the present invention has two or more flow characteristic curve features, and the average flow rate between exv 0-exv 1 is less than or equal to the average flow rate between exv 1-exv 2, the corresponding electronic expansion valve needle 13 has 2 curved surfaces, 0-exv3 is reverse adjustment, the flow rate gradually increases, exv3 has step change around, and the flow rate increases in the moment.

The maximum value of the refrigerant flow rate corresponding to the area S1max of the maximum flow gap between the first needle segment 132 and the orifice 151 is Q2, and the maximum value of the refrigerant flow rate corresponding to the area S2max of the maximum flow gap between the second needle segment 133 and the orifice 151 is Q1, so that Q2/Q1 is 2 ≤ Q2/Q1 ≤ 10. Q2/Q1 can be 2, 4, 6, 8 or 10. Furthermore, Q2/Q1 is more than or equal to 2 and less than or equal to 5.

In the above embodiment, the flow rate of the throttle valve 10 corresponding to the maximum area S1max of the through-flow gap between the first valve needle section 132 and the orifice 151 is Q2, the flow rate of the throttle valve 10 corresponding to the minimum area S2min of the through-flow gap between the second valve needle section 133 and the orifice 151 is Q0, when 0.1Mpa of air is introduced into the throttle valve, 0L/min is equal to or less than Q0 and equal to or less than 8L/min, the rated cooling capacity of the air conditioner is less than 4500W, 10L/min is equal to or less than Q2 and equal to or less than 80L/min, the rated cooling capacity of the air conditioner is in the range of 4500W-14000W, and 20L/min is equal to or less than Q2 and equal to.

The throttle valve 10 detects the air flow under 0.1MPa, the air under 0.1MPa enters the valve cavity 143 from the first inlet and outlet 146 and flows out from the second inlet and outlet 147 through the throttle hole 151, and the technical conditions are met: q0 is more than or equal to 0L/min and less than or equal to 8L/min.

In the above embodiment, the flow rate of the throttle valve 10 corresponding to the maximum area S1max of the flow-through gap between the first valve needle section 132 and the orifice 151 is Q2, the flow rate of the throttle valve 10 corresponding to the maximum area S2max of the flow-through gap between the second valve needle section 133 and the orifice 151 is Q1, the flow rate of the throttle valve 10 corresponding to the minimum area S2min of the flow-through gap between the second valve needle section 133 and the orifice 151 is Q0, the opening degree of the throttle valve 10 corresponding to Q2 is exv2, the opening degree of the throttle valve 10 corresponding to Q1 is exv1, and the opening degree of the throttle valve 10 corresponding to Q0 is exv0, then 150 steps no less than exv1 and no more than 400 steps, 50 steps no less than exv2-exv1 and no more than 350 steps, and 0 steps no less than exv0 and no more.

By controlling the opening of the throttle valve 10 within a certain range, the requirements on Q0, Q1 and Q2 are met, on one hand, the elimination or alleviation of abnormal phenomena of the air conditioner can be ensured by adjusting the throttle valve 10 within the range of exv0, exv1 and exv2, and on the other hand, the adverse effect on the performance of the air conditioner caused by the excessively large increase of the opening of the throttle valve 10 is also prevented.

As shown in fig. 3, the flow rate-opening degree of the throttle valve 10 of the present invention is a curve having two or more flow rate characteristics, and the average flow rate change rate of the refrigerant between exv0 and exv1 is equal to or less than the average flow rate change rate of the refrigerant between exv1 and exv 2. The flow rate of the valve needle 13 before and after the first and second

valve needle segments

132, 133, exv2 having different shapes will be abruptly stepped, momentarily increased, and then maintained constant exv2 < exv 3.

In any of the embodiments described above, the extreme position of movement of the valve seat 15 relative to the valve needle 13 is on the side of the second port 147 facing away from the first port 146.

The limit position (position 3 of the valve seat 15) is located on the side of the second inlet/outlet 147 away from the first inlet/outlet 146, corresponds to the reverse conduction opening exv3, and when the valve seat 15 moves to the position 3 of the valve seat 15 and then continues to move upward, the conduction without the throttle hole 151 can be realized, at this time, the flow area sharply changes, which is similar to a refrigerant bypass without throttling, so that the rapid pressure unloading can be realized, the function of a bypass valve is replaced, and the equipment cost can be correspondingly reduced.

In the above embodiment, in the limit position, the maximum flow rate through the throttle valve 10 is Q3, the maximum flow rate between the second needle section 133 and the orifice 151 is Q1, and Q3/Q1 is 5 or more.

The maximum flow rate Q3 of the refrigerant flowing through the throttle valve 10 corresponds to a state in which the valve seat is moved to the limit position, the first port and the second port communicate with each other through the valve chamber, and do not need to pass through the orifice, and the maximum flow rate Q1 corresponds to a refrigerant flow rate corresponding to the area S2max of the maximum flow gap between the second needle segment 133 and the orifice 151. The ratio of Q3/Q1 is set, and the values of Q3/Q2 and Q2/Q1 can be indirectly adjusted, so that the abnormal condition of the air conditioner can be solved according to the control method in the application.

Furthermore, Q3/Q1 is more than or equal to 20 and less than or equal to 100. Q3 is K2Q 1, and K2 is in the range of 5 to infinity, preferably 20 to 100.

In one embodiment, the baffle opens the bypass hole, the opening degree of the throttle valve 10 is exv3, the flow rate of the throttle valve 10 corresponding to the area S2max of the maximum flow gap between the second valve needle section 133 and the throttle hole 151 is Q1, the opening degree of the throttle valve 10 corresponding to Q1 is exv1, and 150 steps are exv3 to exv1 steps which are 400 steps.

The range of exv3-exv1 is set so that the abnormal situation of the air conditioner can be solved according to the control method in the present application.

In the above embodiment, at the limit position, the opening of the throttle valve 10 is exv3, and 50 steps ≦ 0 to exv3 ≦ 500 steps.

The flow rate is gradually increased by adjusting the flow rates from 0 to exv3 in the reverse direction, and the flow rate is instantly increased by changing the flow rates in steps before and after exv 3. When the valve seat 15 moves to the position 3 of the valve seat 15 and then continues to move upwards, the conduction without the throttling hole 151 can be realized, at the moment, the flow area sharply changes, the flow area is similar to that of a refrigerant bypass without throttling, the pressure can be quickly unloaded, the effect of a bypass valve is replaced, and the equipment cost can be correspondingly reduced.

Aiming at solving the problems that the existing room air conditioner is in solving special scenes, such as high load, low load, frosting, leakage and the like, or the cost is increased, or the production efficiency is low, or the comfort effect is influenced by direct frequency reduction shutdown and the like, a simple and effective solution which is suitable for the room air conditioner is found, and therefore the application provides a throttling valve which can be an electronic expansion valve.

The electronic expansion valve is arranged between the indoor heat exchanger and the outdoor heat exchanger of the air conditioner and has the flow capable of being adjusted in multiple stages.

The electronic expansion valve is specially designed, the valve needle is fixed, the valve seat moves, the valve seat is contacted with the valve body to play a role in throttling and conducting, the movement of the valve seat is controlled by the stepping motor through the connecting rod, the size of the area of the through-flow gap is changed through the adjustment of the opening degree, and the multi-flow rate of change is realized. And the interior of the expansion valve is designed to be communicated, and the valve seat is moved through opening control to realize non-throttling communication. The refrigerant at the valve seat position 0 to the valve seat position 1 changes at a first rate, the refrigerant at the valve seat position 1 to the valve seat position 2 changes at a second rate, and the refrigerant is throttled by the throttle orifice in the previous two stages. The valve seat position 3 corresponds to the reverse conduction opening exv3, and when the valve seat position 3 is moved and then is moved continuously, the conduction without passing through the throttle hole can be realized, and at the moment, the flow area is sharply changed to be similar to that of a refrigerant bypass without throttling.

In any of the above embodiments, one of the first and

second ports

146 and 147 is horizontally disposed and the other is vertically disposed.

As shown in fig. 4(a) and 4(b), the first inlet/outlet 146 is provided at the bottom of the valve body 14 and arranged in the vertical direction, and the second inlet/outlet 147 is provided on the side wall of the valve body 14 and arranged in the horizontal direction, for example. Control requirements for the interval exv 1-exv 2: when the excitation speed of the flow exv 1-exv 2 is equal to or less than 90pps in the direction of the flow from the first port 146 → the second port 147, and when the excitation speed of the flow exv 1-exv 2 is equal to or more than 30pps in the direction of the flow from the second port 147 → the first port 146, the flow from the second port 147 → the first port 146 is preferable.

In the case of a cooling and heating type air conditioner, when cooling and heating are both required, the heating preferably flows in the direction from the second inlet/outlet 147 → the first inlet/outlet 146, that is, the second inlet/outlet 147 is preferably connected to the evaporator, and the first inlet/outlet 146 is preferably connected to the condenser (although the first inlet/outlet 146 is connected to the evaporator, and the second inlet/outlet 147 may be connected to the condenser, it is necessary to control the excitation speed).

In any of the above embodiments, the driving device includes the motor 12, the throttle valve 10 includes a connecting rod 152, one end of the connecting rod 152 is connected to a motor shaft of the motor 12, the other end of the connecting rod 152 is connected to the valve seat 15, a sleeve 141 is connected to the valve body 14, and the connecting rod 152 is located in the sleeve 141 and is in threaded connection with the sleeve 141, so that the motor 12 drives the connecting rod 152 to rotate to drive the valve seat 15 to move relative to the valve needle 13 along the axial direction of the valve needle 13.

The coil 121 and the magnet 122 provided outside the valve body 14 cooperate with each other to correspond to the motor 12, and constitute a drive device for the valve seat. When the flow rate of the throttle valve 10 needs to be adjusted and changed, an appropriate pulse signal is applied to the coil 121, the magnet 122 is driven by the coil 121 to rotate, the connecting rod 152 is driven to rotate together, the connecting rod 152 and the sleeve 141 sleeved outside the connecting rod 152 form a threaded fit, and the sleeve 141 is fixed on the valve body 14, so that the connecting rod 152 axially moves up and down while rotating, the valve seat 15 is driven to move up and down, the throttling hole 151 in the valve seat 15 moves up and down relative to the throttling part 131, the flow rate of refrigerant passing through the throttling hole 151 is changed, and the flow rate of the refrigeration system is controlled. The sleeve 144 is provided with a positioning member 142 for limiting the displacement of the connecting rod 152 in the radial direction, which can provide a stabilizing effect. For example, the driving device includes a motor 12, a gear is connected to a motor shaft of the motor 12, and a rack is connected to the valve needle 13, and the gear is engaged with the rack, so that the motor 12 drives the valve needle 13 to move along the axial direction of the valve needle 13 relative to the valve seat 15.

The motor 12 includes a coil 121 (stator), a magnet 122 (rotor) positioned inside the coil 121, a connection portion 134 of the needle 13 connected to the magnet 122 and positioned inside the magnet 122, and a spring 11 supported between a tip end of the connection portion 134 and the magnet 122. Further, the motor 12 is a stepper motor 12.

Or, the driving device includes a motor, the throttle valve includes a connecting rod 152, one end of the connecting rod 152 is connected with a motor shaft of the motor 12, the other end of the connecting rod 152 is connected with the valve seat 15, the valve body is connected with the positioning member 142, the valve needle is connected with the sleeve 144, the sleeve 144 is located in the positioning member 142 and is in threaded connection with the positioning member 142, so that the motor drives the connecting rod and the valve seat to rotate to drive the valve seat to move relative to the valve needle.

The motor 12 can drive the valve seat 15 to reciprocate up and down relative to the valve needle 13 by driving the valve seat 15 to rotate, and the motor 12 can also drive the valve seat 15 to reciprocate up and down relative to the valve needle 13 by meshing of a gear and a rack without rotating the connecting rod 152.

Example two:

the difference from the first embodiment is that, as shown in fig. 12, the valve body 14 includes an outer layer 145 and an inner layer 144 which are spaced apart from each other, the inner layer 144 defines a valve cavity 143, a bypass space 148 is defined between the inner layer 144 and the outer layer 145, a bypass hole 149 is provided on the inner layer 144, the bypass hole 149 communicates the bypass space 148 with the valve cavity 143, and the first inlet/outlet 146 penetrates through the inner layer 144 and the outer layer 145 and communicates with the bypass space 148; the valve seat 15 moves relative to the valve needle 13 to open or close the bypass hole 149, wherein the valve needle 13 escapes from the orifice 151, and the valve seat 15 opens the bypass hole 149.

A first passageway 146 extends through inner layer 144 and through outer layer 145 such that first passageway 146 communicates with bypass space 148 and with valve chamber 143. When the valve seat 15 opens the bypass hole 149, the refrigerant flowing from the first port 146 may flow into the second port 147 through the valve chamber 143, and the refrigerant flowing from the first port 146 may flow into the bypass hole 149 through the bypass space 148 and flow into the second port 147 through the valve chamber 143. After the bypass hole 149 is opened, the refrigerant can enter the valve cavity 143 from the bypass hole 149, so that the inflow amount of the refrigerant in the valve cavity 143 is increased, and the throttling effect can be weakened.

Further, when the orifice 131 is disengaged from the orifice 151 and the valve seat 15 continues to move in a direction away from the needle 13 (downward in fig. 12) after the orifice 131 is disengaged from the orifice, the valve seat 15 opens the bypass hole 149, and at this time, the flow area sharply changes, the amount of refrigerant flowing into the valve chamber 143 is instantaneously increased, and the refrigerant bypass operation is approximated.

As shown in fig. 12, the needle 13 is fixed, the valve seat 15 moves, the valve seat 15 contacts the valve body 14 to seal and open the bypass hole 149, the movement of the valve seat 15 is controlled by the stepping motor through the connecting rod 152, and the size of the orifice 151 is changed through the adjustment of the opening degree, thereby realizing the multi-flow rate change. And the design has the inside bypass of choke valve 10, through opening control, removes valve seat 15, realizes the bypass before and after the throttle, weakens the throttle effect. The refrigerant at the valve seat position 0 to the valve seat position 1 changes at a first rate, the refrigerant at the valve seat position 1 to the valve seat position 2 changes at a second rate, the refrigerant is throttled by the throttling hole 151 in the previous two stages, when the body moves to the valve seat position 2 and then moves continuously, the bypass holes 149 on the two sides can be opened, at the moment, the flow area is changed sharply, and the refrigerant is similar to the bypass of the refrigerant without throttling.

In one embodiment, as shown in FIG. 13, the valve seat 15 opens the bypass hole 149, the maximum flow through the throttle 10 is Q4, the maximum flow between the second needle section 133 and the orifice 151 is Q1, and Q4/Q1 is 5 or more.

The maximum flow rate Q4 of the refrigerant flowing through the throttle valve 10 corresponds to a state in which the throttle portion 131 is disengaged from the orifice 151 and the bypass hole 149 is fully opened, and the state corresponding to Q1 corresponds to a refrigerant flow rate corresponding to the maximum flow area S2max between the second valve needle segment 133 and the orifice 151. The ratio of Q4/Q1 is set, and the values of Q4/Q2 and Q2/Q1 can be indirectly adjusted, so that the abnormal condition of the air conditioner can be solved according to the control method in the application.

Furthermore, Q4/Q1 is more than or equal to 20 and less than or equal to 100.

In one embodiment, the valve seat 15 opens the bypass hole 149, the opening degree of the throttle valve 10 is exv4, the flow rate of the throttle valve 10 corresponding to the maximum flow area S2max between the second valve needle section 133 and the throttle hole 151 is Q1, and the opening degree of the throttle valve 10 corresponding to Q1 is exv1, and then 150 steps are exv4 to exv1 steps are 400 steps.

As shown in fig. 5 and 6, an embodiment of a second aspect of the present invention provides an air conditioner, including: a compressor 21 having an exhaust port 211 and a return port 212; a four-way valve 22 having first to fourth ports, one of the first and third ports being communicated with the second port, the other of the first and third ports being communicated with the fourth port, the first port being connected to the exhaust port 211, and the third port being connected to the return air port 212; an indoor heat exchanger 26 and an outdoor heat exchanger 24, a second port being connected to a first end of the indoor heat exchanger 26, a fourth port being connected to a first end of the outdoor heat exchanger 24; the throttle valve 10 as in any one of the embodiments of the first aspect, the throttle valve 10 is connected in series between the second end of the indoor heat exchanger 26 and the second end of the outdoor heat exchanger 24.

The embodiment of the second aspect of the present invention provides an air conditioner, which includes the throttle valve 10 of any one of the embodiments of the first aspect, and therefore has all the advantages of the throttle valve 10 of any one of the embodiments, and is not repeated herein.

The throttling valve 10, the flow characteristic curve and the control logic are matched, the multi-use scene requirements of different refrigeration and heating of the air conditioner can be met respectively, and the multi-use scene requirements of different refrigeration and heating of the air conditioner can be met respectively only by one throttling valve 10.

In the above embodiment, the air conditioner includes: and an auxiliary heater 27 disposed adjacent to the indoor heat exchanger 26 for heating the indoor heat exchanger 26.

The indoor unit includes an indoor heat exchanger 26, an indoor fan 25, and an auxiliary heater 27 to turn on auxiliary heating of the room when a defrosting operation is performed. For the cooling and heating type, when the indoor unit is provided with the auxiliary heater 27, the auxiliary heater 27 can be forcibly powered on when the defrosting is performed through heating, so that the auxiliary heater 27 works, and the defrosting effect without reversing is improved.

Further, an auxiliary heater 27 is located between the indoor fan 25 and the indoor heat exchanger 26. An outdoor fan 23 is arranged at the outdoor heat exchanger 24.

Further, horizontally disposed one of the first and

second ports

146 and 147 of the throttle valve is connected to the indoor heat exchanger 26, and vertically disposed one is connected to the outdoor heat exchanger 24.

Taking the first doorway 146 as a vertical installation and the second doorway 147 as a horizontal installation, the control requirements for the section exv1 to exv2 are as follows: when the excitation speed of the flow exv 1-exv 2 is equal to or less than 90pps in the direction of the flow from the first port 146 → the second port 147, and when the excitation speed of the flow exv 1-exv 2 is equal to or more than 30pps in the direction of the flow from the second port 147 → the first port 146. Therefore, in the cooling and heating type air conditioner, the refrigerant flow direction during heating is selected from the second outlet 147 to the first outlet 146. It is to be understood that the refrigerant flow direction during heating may be from the first inlet/outlet 146 to the second inlet/outlet 147, and in this case, the first inlet/outlet 146 is connected to the indoor heat exchanger 26 and the second inlet/outlet 147 is connected to the outdoor heat exchanger 24, but it is necessary to take care to control the excitation speed.

The third embodiment of the present invention provides a control method, which depends on the structure of the air conditioner described in the second embodiment, and of course, there is a control mechanism, which is not shown in fig. 5 and 6 as a general component.

The air conditioner of the application comprises a basic sensor for collecting the following parameters, namely indoor room temperature, indoor coil temperature, outdoor environment temperature, outdoor coil temperature, exhaust temperature and the like.

And then, whether the conditions are met or not is judged according to the parameters, the control and adjustment of the electronic expansion valve are started, if so, the opening of the electronic expansion valve is adjusted according to the corresponding control logic and the frequency of the compressor 21, so that the requirements on reliability or comfort are met.

The control method for solving the high-pressure and low-pressure unloading of the throttle valve corresponding to the first embodiment is shown in fig. 7, the control method for solving the problem of the overhigh exhaust temperature (leakage and blockage) is shown in fig. 8, the control method for alleviating heating frost formation is shown in fig. 9, the control method for solving the problem of the heating frost formation is shown in fig. 10, and the control method for solving the problem of the too low shutdown temperature fluctuation of the refrigeration load is shown in fig. 11.

Corresponding to the throttle valve described in the second embodiment, a control method for solving high-low pressure unloading is shown in fig. 14, a control method for solving excessive exhaust temperature (leakage and blockage) is shown in fig. 15, a control method for alleviating heating frost formation is shown in fig. 16, a control method for solving heating frost formation is shown in fig. 17, and a control method for solving too low shutdown temperature fluctuation of refrigeration load is shown in fig. 18.

In summary, the throttle valve 10 according to the embodiment of the present invention is provided with a specific limitation on the opening degree adjustment process of the throttle valve 10, that is, the opening degree adjustment is performed from the initial opening degree exv0, and the opening degree adjustment of the throttle device at least includes two stages, where the first stage is from the initial opening degree to the first opening degree exv1, and the second stage is from the first opening degree exv1 to the second opening degree exv2, the first stage increases the refrigerant flow rate at a first rate, the second stage increases the refrigerant flow rate at a second rate, and the second rate is greater than the first rate, on one hand, when the current abnormal problem cannot be solved or alleviated after the refrigerant flow rate is increased at the first rate, the abnormal problem can be solved or alleviated by further adjusting the opening degree of the throttle device at the second rate, on the other hand, compared with the solution of the related art, a bypass for performing the unloading operation does not need to be separately provided, and therefore, the manufacturing cost, in a further aspect, in contrast to the solutions of the related art, no shutdown operations need to be performed, and therefore normal use by the user is not affected.

In the description of the present invention, the term "plurality" means two or more unless explicitly stated or limited otherwise; the terms "connected," "secured," and the like are to be construed broadly and unless otherwise stated or indicated, and for example, "connected" may be a fixed connection, a removable connection, an integral connection, or an electrical connection; may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the description of the present invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or unit indicated must have a specific direction, be constructed in a specific orientation, and be operated, and therefore, should not be construed as limiting the present invention.

In the description of the present specification, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A throttle valve, comprising:

the valve body is provided with a first inlet and a second inlet which are communicated with the valve cavity;

the valve seat is positioned in the valve cavity, and an orifice is arranged on the valve seat;

the valve needle is positioned in the throttling hole;

the driving device is connected with the valve seat so as to drive the valve seat to move relative to the valve needle;

the valve needle comprises a throttle portion comprising a first needle section and a second needle section, the throttle portion being locatable within the throttle bore, the first inlet/outlet and the second inlet/outlet communicate with each other through a flow gap between the throttle portion and the throttle hole in a direction from the first needle section to the second needle section, the rate of change of the area S1 of the flow gap between the first needle section and the orifice differs from the rate of change of the area S2 of the flow gap between the second needle section and the orifice, the driving device drives the throttle hole to move relative to the throttle part so as to change the change rate of the area of the through-flow gap between the throttle part and the throttle hole, wherein the first valve needle section and the second valve needle section are arranged in sequence along a direction of movement of the valve needle relative to the valve seat.

2. The throttling valve of claim 1,

the valve needle comprises a connecting part, the connecting part and the throttling part are sequentially arranged along the axial direction of the valve needle, the connecting part is connected to the valve body, the second valve needle section is arranged between the first valve needle section and the connecting part, and the change rate of the area S1 of the through-flow gap between the first valve needle section and the throttling hole is larger than the change rate of the area S2 of the through-flow gap between the second valve needle section and the throttling hole.

3. The throttling valve of claim 1,

in a direction from the first valve needle section to the second valve needle section, the cross-sectional area of the first valve needle section gradually increases, and the area S1 of the through-flow gap between the first valve needle section and the orifice gradually decreases, so that the rate of change of the area S1 of the through-flow gap is constant.

4. The throttling valve of claim 1,

in a direction from the first needle section to the second needle section, the cross-sectional area of the second needle section gradually increases, and the area S2 of the through-flow gap between the second needle section and the orifice gradually decreases, so that the rate of change of the area S2 of the through-flow gap is constant.

5. The throttling valve of claim 1,

the area S1 of the flow gap between the first needle section and the throttle bore is greater than the area S2 of the flow gap between the second needle section and the throttle bore.

6. The throttling valve of claim 1,

the outer wall surface of the first valve needle section is in a convex cambered surface shape or a conical shape.

7. The throttling valve of claim 1,

the outer wall surface of the second valve needle section is in a convex cambered surface shape or a circular truncated cone shape.

8. The throttling valve of claim 1,

the maximum area of the through-flow gap between the first valve needle section and the throttle hole is S1max, the maximum area of the through-flow gap between the second valve needle section and the throttle hole is S2max, and S1max/S2max is more than or equal to 2 and less than or equal to 10.

9. The throttling valve of claim 1,

the flow rate of the throttle valve corresponding to the maximum area S1max of the through-flow gap between the first valve needle section and the throttle hole is Q2, the flow rate of the throttle valve corresponding to the minimum area S2min of the through-flow gap between the second valve needle section and the throttle hole is Q0, 0.1Mpa air is introduced into the throttle valve, 0L/min is not less than Q0 and not more than 8L/min, the rated refrigerating capacity of the air conditioner is less than 4500W, 10L/min is not less than Q2 and not more than 80L/min, the rated refrigerating capacity of the air conditioner is in the range of 4500W-14000W, and 20L/min is not less than Q2 and not more than 150L/min.

10. The throttling valve of claim 1,

the flow rate of the throttle valve corresponding to the maximum area S1max of the through-flow gap between the first valve needle section and the throttle hole is Q2, the flow rate of the throttle valve corresponding to the maximum area S2max of the through-flow gap between the second valve needle section and the throttle hole is Q1, the flow rate of the throttle valve corresponding to the minimum area S2min of the through-flow gap between the second valve needle section and the throttle hole is Q0, the opening degree of the throttle valve corresponding to Q2 is exv2, the opening degree of the throttle valve corresponding to Q1 is exv1, the opening degree of the throttle valve corresponding to Q0 is exv0, then 150 steps are not less than exv1 and not more than 400 steps, 50 steps are not less than exv2-exv1 and not more than 350 steps, and 0 step not less than exv0 and not more than 100 steps.

11. The throttling valve according to any of claims 1 to 10,

the extreme position of the valve seat in relation to the movement of the valve needle is located on the side of the second port facing away from the first port.

12. The throttling valve of claim 11,

in the limit position, the maximum flow through the throttle is Q3, the maximum flow between the second needle section and the throttle bore is Q1, and Q3/Q1 is 5 or more.

13. The throttling valve of claim 11,

at the limit position, the opening degree of the throttle valve is exv3, and 50 steps are less than or equal to 0-exv3 and less than or equal to 500 steps.

14. The throttling valve according to any of claims 1 to 10,

the valve body comprises an outer layer and an inner layer which are spaced, the valve cavity is defined by the inner layer, a bypass space is defined between the inner layer and the outer layer, a bypass hole is arranged on the inner layer and is communicated with the bypass space and the valve cavity, and the first inlet and the first outlet penetrate through the inner layer and the outer layer and are communicated with the bypass space;

the valve seat moves relative to the valve needle to open or close the bypass hole, wherein the valve needle is withdrawn from the orifice, and the valve seat opens the bypass hole.

15. The throttling valve of claim 14,

the valve seat opens the bypass hole, the maximum flow rate flowing through the throttle valve is Q4, the maximum flow rate between the second valve needle section and the throttle hole is Q1, and Q4/Q1 is more than or equal to 5.

16. The throttling valve of claim 14,

the valve seat opens the bypass hole, the opening degree of the throttle valve is exv4, the flow rate of the throttle valve corresponding to the maximum flow area S2max between the second valve needle section and the throttle hole is Q1, the opening degree of the throttle valve corresponding to Q1 is exv1, and then 150 steps are not more than exv4-exv1 steps are not more than 400 steps.

17. The throttling valve according to any of claims 1 to 10,

one of the first access opening and the second access opening is horizontally arranged, and the other is vertically arranged.

18. The throttling valve according to any of claims 1 to 10,

the driving device comprises a motor, the throttle valve comprises a connecting rod, one end of the connecting rod is connected with a motor shaft of the motor, the other end of the connecting rod is connected with the valve seat, a sleeve is connected onto the valve body, the connecting rod is positioned in the sleeve and is in threaded connection with the sleeve, or the valve body is connected with a positioning piece, the valve needle is connected with a sleeve, the sleeve is positioned in the positioning piece and is in threaded connection with the positioning piece, so that the motor drives the connecting rod and the valve seat to rotate to drive the valve seat to move relative to the valve needle; or

The driving device comprises a motor, a gear is connected to a motor shaft of the motor, a rack is connected to the valve seat, and the gear is meshed with the rack so that the motor drives the valve seat to move relative to the valve needle.

19. An air conditioner, comprising:

a compressor having a discharge port and a return port;

a four-way valve having a first port connected to the exhaust port and a fourth port connected to the return air port;

the first end of the indoor heat exchanger is connected with the second port, and the first end of the outdoor heat exchanger is connected with the fourth port;

the throttle valve of any one of claims 1 to 18, being connected in series between the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger.

20. The air conditioner as claimed in claim 19, comprising:

and the auxiliary heater is arranged close to the indoor heat exchanger and used for heating the indoor heat exchanger.

21. The air conditioner according to claim 19 or 20,

one of the first inlet and the second inlet of the throttle valve, which is horizontally arranged, is connected with the indoor heat exchanger, and the other one of the first inlet and the second inlet of the throttle valve, which is vertically arranged, is connected with the outdoor heat exchanger.