EP1170505A2

EP1170505A2 - Vacuum Pump

Info

Publication number: EP1170505A2
Application number: EP01116244A
Authority: EP
Inventors: Hironao Numoto; Junichi Nishda
Original assignee: Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Holdings Corp
Priority date: 2000-07-04
Filing date: 2001-07-04
Publication date: 2002-01-09
Anticipated expiration: 2021-07-04
Also published as: EP1170505B1; EP1170505A3; CN2485447Y; JP2002021723A; ES2231349T3; JP3264277B2

Abstract

A suction check valve 18a and a discharge check valve 20a are disposed to a top end plate of a cylinder 14. A suction check valve 18b and a discharge check valve 20b are disposed to a bottom end plate in the like manner. The suction check valves 18a and 18b are joined together into one hose for connection to an indoor unit B. A piston 15 divides an interior of the cylinder 14 into two chambers, an upper chamber 14A and a lower chamber 14B. The upper chamber 14A and the lower chamber 14B alternately suction air from the indoor unit B through the suction check valves 18a and 18b, and discharge the suctioned air to outer space through the discharge check valves 20a and 20b, when the piston 15 is reciprocated. Thus, the indoor unit B is decompressed in preparation for charging refrigerant gas.

Description

FIELD OF THE INVENTION

The present invention relates to a vacuum pump. In particular, it relates to a vacuum pump used for suctioning air from an indoor unit of air conditioner prior to charging the indoor unit with refrigerant gas during installation of the air conditioner.

BACKGROUND OF THE INVENTION

Charging of an indoor unit with refrigerant gas has been made heretofore in a manner that a main outdoor unit is filled with an amount of refrigerant gas that is more than the regular amount with an extra portion reserved for air-purge, the refrigerant gas is used to expel air in the indoor unit and its connecting tubes through a two-way valve on a liquid side, and thereby the air is discharged into the atmosphere together with the refrigerant gas from a service port in a three-way valve on a gas side. However, this charging method releases the refrigerant gas into the atmosphere, which is the concern for depletion of ozone layer and global warming. Another charging method using a motor-driven vacuum pump is a method, in which refrigerant gas is introduced into connecting tubes and the indoor unit through the two-way valve on the liquid side, after the connecting tubes and the indoor unit are decompressed sufficiently by suctioning air with the motor-driven vacuum pump from the service port in the three-way valve on the gas side. This charging method using the motor-driven vacuum pump is desirable because it does not release the refrigerant gas into the atmosphere. However, it is quite difficult to use the motor-driven vacuum pump on such place as rooftop where the work condition is not right. In addition, the charging method using motor-driven vacuum pump generally takes a longer time as compared to the charging method using the refrigerant gas in the outdoor unit to purge air .

SUMMARY OF THE INVENTION

The present invention is intended to provide an easy-to-use vacuum pump that simplifies the work of suctioning air from the indoor unit.

In a vacuum pump of the present invention, there are provided with a suction check valve and a discharge check valve attached to a top end plate of a cylinder. In the like manner, another suction check valve and another discharge check valve are also attached to a bottom end plate. The suction check valve on the top end plate and the suction check valve on the bottom end plate are connected together into one hose, which is then connected to an indoor unit. Both the discharge check valve on the top end plate and the discharge check valve on the bottom end plate are kept open to the outer space. A piston divides an interior of a cylinder into two chambers, an upper chamber and a lower chamber. When the piston is forced to reciprocate, the upper chamber and the lower chamber in the cylinder suction air alternately from the indoor unit through the suction check valves, and discharge the suctioned air to the outer space through the discharge check valves. Subsequently, as the piston continues its reciprocal motion, a difference in pressure between the two chambers decreases gradually from the initial start, and the interior of the cylinder and the indoor unit is decompressed sufficiently. Using the vacuum pump of this invention, there can be achieved a reduction of deleterious oxygen in the air remaining in the refrigeration cycle to a level sufficient to maintain reliability of the refrigeration cycle, and completion of installing the air conditioner within a short period of time. Besides, the vacuum pump of this invention can be operated manually.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1 is a diagrammatic illustration of an air conditioner in connection with an exemplary embodiment of the present invention;

Fig. 2 is a schematic view depicting a vacuum pump of an exemplary embodiment of this invention, and hose connections thereto;

Fig. 3 is a sectional view of a check valve used in this exemplary embodiment of the invention;

Fig. 4 is a sectional view of the check valve taken along a line A-A in Fig. 3;

Fig. 5 is a schematic illustration showing an example of shaft seal in the vacuum pump of this invention;

Fig. 6 is a structural illustration of a filter used in the exemplary embodiment of this invention;

Fig. 7 is a graph showing a relation between number of piston strokes and internal pressure of a cylinder as measured in a third exemplary embodiment of this invention;

Fig. 8 is a schematic view depicting hose connections routing a vacuum pump of a fourth exemplary embodiment of this invention;

Fig. 9 is a structural illustration of a check valve used in the fourth exemplary embodiment of this invention;

Fig. 10 is an enlarged view showing an essential portion of the vacuum pump of Fig. 8;

Fig. 11 is a schematic illustration showing another example of shaft seal in the vacuum pump of this invention;

Fig. 12 is a structural illustration of an airflow detector used in the exemplary embodiments of this invention;

Fig. 13 is a structural illustration of another airflow detector; and

Fig. 14 is a structural illustration of still another airflow detector.

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Exemplary Embodiment)

Fig. 1 illustrates an overall configuration of a split type air conditioner of this exemplary embodiment. An outdoor unit A is provided with a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, a choking unit 4, a drier 5, a two-way valve 7 on liquid side, and a three-way valve 8 on gas side. An indoor unit B is provided with an indoor heat exchanger 6.

The drier 5 removes moisture present in the indoor unit B and connecting tubes 9 and 10. The connecting tubes 9 and 10 used for connecting the outdoor unit A and the indoor unit B are connected respectively to the two-way valve 7 on the liquid side and the three-way valve 8 on the gas side of the outdoor unit A. The two-way valve 7 on the liquid side is provided with a threaded tap 7a, and the connecting tube 9 is connected to the outdoor unit A by opening this threaded tap 7a. On the other hand, the three-way valve 8 on the gas side is provided with a threaded tap 8a and a service port 8b, and the connecting tube 10 is connected to the outdoor unit A by opening this threaded tap 8a.

Fig. 2 shows a structure of a vacuum pump and hose connections necessary for the operation of charging refrigerant gas. A center port 12a of a gauge manifold 12 is connected to the service port part 8b in the three-way valve 8 on the gas side with a pressure-tight hose 11, and a low-pressure side port 12b of the gauge manifold 12 is connected to the vacuum pump with another pressure-tight hose 13. A piston 15 of the vacuum pump is placed within a cylinder 14 made of aluminum in a manner that it divides an interior of the cylinder 14 into two chambers. The piston 15 is connected with a manual handlebar 17 via a piston shaft 16 made of stainless steel which extends from an upper surface of it. Suction /

discharge ports

14a and 14b are disposed respectively to exterior surfaces of the top end plate and the bottom end plate of the cylinder 14. The suction / discharge port 14a connects the cylinder 14 to the low-pressure side port 12b of the gauge manifold 12 through a suction check valve 18a, a filter 19a, and the pressure-tight hose 13. The suction check valve 18a stops discharge air from the cylinder 14, but it passes only air suctioned into the cylinder 14. A discharge check valve 20a, which diverges from there, stops air from being suctioned into the cylinder 14, and passes only the air discharged from the cylinder 14. The suction / discharge port 14b connects the cylinder 14 to the low-pressure side port 12b of the gauge manifold 12 through a suction check valve 18b, another filter 19b, and the pressure-tight hose 13. The suction check valve 18b stops air discharged from the cylinder 14, but it passes only air suctioned into the cylinder 14. A discharge check valve 20b, which diverges from there, stops air from being suctioned into the cylinder 14, and passes only the air discharged from the cylinder 14.

Fig. 3 and 4 depict a structure of the

check valves

18a, 18b, 20a, and 20b. A copper tube 181 is provided with roll-formed grooves in two locations, and a valve retainer seat 182 made of brass is fixed to a groove 181a. When there is a flow of air in a direction shown by an arrow, the airflow is not obstructed, although a valve body 183 made of nylon is pressed against a groove 181b by the airflow. When the air flows in an opposite direction of the arrow, the nylon valve body 183 stops the airflow, as it is pressed against the valve retainer seat 182 by the airflow. Thus, the air flows only in the direction of the arrow.

As shown in Fig. 5, there are O-

rings

21a and 21b disposed doubly to a part of the top end plate of the cylinder 14, where the piston shaft 16 penetrates through, for sealing the shaft. The double O-ring prevents foreign particles, which tend to cause bites into the O-rings, from adhering to the piston shaft 16.

Fig. 6 shows an internal structure of the filter 19. The filter 19 has a cylindrical configuration. The air entering inside of the filter 19 is deflected into radial direction as it immediately strikes on a wall, and eventually led to an exit after passing through a pulp film 191 placed in it. The pulp film 191 thus catches dust. In addition, the dust caught in it can be examined visually, if the cylinder of the filter 19 is made of glass or resin having transparency.

The piston 15 is moved to reciprocate between a top position and a bottom position in the cylinder 14. When the manual handlebar 17 is pulled to shift the piston 15 toward a direction "A", air in the indoor unit B and the connecting tube 9 is pulled into a lower chamber 14B within the cylinder from the service port 8b through the pressure-tight hose 11, the gauge manifold 12, the pressure-tight hose 13, the filter 19b, the suction check valve 18b and the suction / discharge port 14b. On the other hand, air in an upper chamber 14A within the cylinder is discharged into the outer space from the suction / discharge port 14a through the discharge check valve 20a. Next, when the manual handlebar 17 is pushed to move the piston 15 toward another direction "B", air in the indoor unit B and the connecting tube 9 is pulled into the cylinder chamber 14A from the service port 8b through the pressure-tight hose 11, the gauge manifold 12, the pressure-tight hose 13, the filter 19b, the suction check valve 18a and the suction / discharge port 14a. On the other hand, air within the cylinder chamber 14B is discharged into the atmosphere from the suction / discharge port 14b through the discharge check valve 20b. The interior of the cylinder is continuously decompressed in this manner, regardless of which direction the piston 15 is moved between the direction "A" and the direction "B". A satisfiable state of negative pressure can be attained eventually by repeating the reciprocating motion of the piston 15.

In the initial stage of using the vacuum pump, there produces a large difference in pressure between the upper chamber 14A and the lower chamber 14B within the cylinder. However, this difference of pressure decreases gradually as the piston continues to reciprocate. The shaft seal is doubled with the O-rings in order to maintain sufficiently the difference in pressure between the negative pressure (30torr or less) within the cylinder 14 and the atmosphere (760torr), and to keep the leakage of air as small as possible (Fig. 5).

The following procedure describes the work involved in charging the indoor unit with refrigerant gas, using the vacuum pump of this invention.

1) The pressure-tight hose 11 is connected at its one end to the service port 8b, to make it in continuity with the indoor unit B, and the connecting tubes 9 and 10, as shown in Fig. 1. Another end of the pressure-tight hose 11 is connected with a center port 12a of the gauge manifold 12, as shown in Fig. 2. The pressure-tight hose 13 is connected at its one end to a low-pressure side port 12b of the gauge manifold 12, and another end to the hoses of the vacuum pump. A low-pressure side knob 12c of the gauge manifold 12 is turned to an open position to render the pressure-tight hose 13 in communication with the pressure-tight hose 11.

2) As the manual handlebar 17 is reciprocated in the directions of "A" and "B", the interior of the cylinder 14, and therefore the interiors of the indoor unit B and the connecting tubes 9 and 10, gradually reaches a state of sufficient negative pressure. This state of sufficient negative pressure is checked with a low-pressure gauge 12d on the gauge manifold 12. The low-pressure side knob 12c of the gauge manifold 12 is turned to a close position immediately thereafter.

3) An internal pressure of the connecting tubes 9 and 10, and tubing in the indoor unit B is raised by a small extent (approx. 0.2 kgf/cm²) by slightly loosening the threaded tap 7a of the two-way valve 7 on the liquid side, and introducing refrigerant gas from the outdoor unit A.

4) The pressure-tight hose 11 is detached from the service port 8b, and the threaded tap 7a of the two-way valve 7 on the liquid side is turned open completely. Finally, a threaded tap 8a of the three-way valve 8 on the gas side is also opened completely.

Here, a ratio of C1/C2 defines an efficiency value of the vacuum pump of this invention, in which C1 represents a capacity bounded from a lower surface of the piston to the two

check valves

18b and 20b when the piston is at its top position, and C2 represents another capacity from the lower surface of the piston to the two

check valves

18b and 20b when the piston is at its bottom position.

As described above, the vacuum pump of this invention uses the upper chamber formed above the piston and the lower chamber formed below the piston, to suction air from the indoor unit. An air suctioning efficiency of the upper chamber is smaller than that of the lower chamber, because a maximum capacity of the upper chamber is smaller than that of the lower chamber by a portion of the space occupied by the piston shaft. It is desirable to increase the capacity from the upper surface of the piston to the two

check valves

18a and 20a, when the piston is at its top position, nearly equal to the C2 capacity, in order to bring up the air suctioning efficiency of the upper chamber close to that of the lower chamber.

(Second Exemplary Embodiment)

In this exemplary embodiment, an interior volume of indoor unit B, including an indoor heat exchanger 6, and connecting tubes 9 and 10 measures 1.5 liters. The capacities C1 and C2 that determine an efficiency value of the vacuum pump are: C1 = 205ml; and C2 = 5ml. Of the capacity C1, a capacity of the cylinder is 200ml (i.e. 27mm in diameter by 350mm). An efficiency value of the vacuum pump is thus calculated as C1/C2 = 205/5 = 41. The interior of the cylinder can be decompressed to 30torr, when operated according to the steps 1) and 2) of the above-described procedure for charging refrigerant gas.

(Third Exemplary Embodiment)

In this exemplary embodiment, an interior volume of indoor unit B, including an indoor heat exchanger 6, and connecting tubes 9 and 10 measures 1.5 liters. The capacities C1 and C2 that determine an efficiency value of the vacuum pump are: C1 = 302ml; and C2 = 5ml. Of the capacity C1, a capacity of the cylinder is 297ml (i.e. 29mm in diameter by 450mm). An efficiency value of the vacuum pump is calculated as C1/C2 = 302/5 = 60.4. The interior of the cylinder can be decompressed to 22torr, when operated according to the steps 1) and 2) of the above-described procedure for charging refrigerant gas.

A progress of decompression in this opertion is shown in Fig. 7 with a relation between number of strokes and internal pressure. For the refrigeration cycles of the second and the third exemplary embodiments containing refrigerant of R410A and refrigeration oil of ester group, reliability tests were performed for 5000 hours under the conditions that a discharge temperature from the compressor is set to 115°C, and both the indoor unit and the outdoor unit are kept at 40°C as a high-temperature cooling condition. No abnormality of especial importance was produced as the result.

(Fourth Exemplary Embodiment)

Fig. 8 shows hose connections of the vacuum pump of this exemplary embodiment. Like numerals have been used throughout to represent like components as in Fig. 2, and their description will be skipped.

In this exemplary embodiment, a gauge manifold 12 and a pressure-tight hose 11 are omitted as opposed to that shown in Fig. 2, and a pressure-tight hose 13 is connected to the service port 8b shown in Fig. 1. A discharge check valve 23a and a suction check valve 25a are mounted directly to a top end plate of a cylinder, and another discharge check valve 23b and anther suction check valve 25b are mounted directly to a bottom end plate of the cylinder.

Airflow detectors

24a and 24b are attached to the

discharge check valves

23a and 23b respectively. The above-described structure shown in Fig. 3 and 4 is employed for the

discharge check valves

23a and 23b. The structure shown in Fig. 9 is employed for the

suction check valves

25a and 25b.

Fig. 9 depicts a longitudinal section of the suction check valve, in which grooves are roll-formed in a copper pipe 231 at two places. A valve retainer seat 232 made of brass is fixed to one groove 231a, and another valve retainer seat 235 also made of brass is fixed to another groove 231b. A thin plate 234 made of nylon film and connected to a helical spring 233 is thrust against the valve retainer seat 235 with the spring force to block an airflow passage in an opposite direction of an arrow. Therefore, the air flows only in a direction of the arrow when the air pressure exceeds the force of spring. An airflow passage in the upstream side of the valve retainer seat 235 is tapered to increase the air pressure to some extent by throttling the suctioned air.

In this exemplary embodiment, capacities C1 and C2 that determine an efficiency value of the vacuum pump are: C1 = 203.5ml; and C2 = 3.5ml. Of the capacity C1, a capacity of the cylinder is 200ml (i.e. 27mm in diameter by 350mm). An efficiency value of the vacuum pump is calculated as C1/C2 = 203.5/3.5 = 58.1.

Fig. 10 shows definitively the capacity C2 bounded from a lower surface of the piston 15 to the suction check valve 25b and the discharge check valve 23b when the piston 15 is at its lowest position. This exemplary embodiment reduces the capacity C2, by mounting the suction check valve 25b and the discharge check valve 23b directly to the bottom end plate of the cylinder 14.

A ring 21 C having a gourd-shaped cross section is placed as a shaft seal in a part where the piston shaft 16 penetrates the top end plate of the cylinder 14, as shown in Fig. 11. The gourd-shaped ring 21 C seals the shaft doubly.

Fig. 12 depicts an internal structure of

flow detectors

24a and 24b. A shaft 241 is positioned in a center of a film 242 along its orthogonal direction. An arrow indicates a direction of airflow from the cylinder to a discharge port. The film 242 moves when air from the check valve strikes upon it. An operator is able to see if there still exists a certain amount of air to be discharged by observing a movement of the film 242. He then stops operation of the vacuum pump when he so judges that there hardly is any air remaining to be discharged from the discharge port. In this exemplary embodiment, it is judged that there hardly exists any air to be discharged from the discharge port, when an internal pressure of the cylinder reaches 20torr or lower.

Other airflow detectors having such internal structures as shown in Fig. 13 and 14 may also be used. In Fig. 13, a silicone film 244 is arranged in a manner to confront the direction of airflow. The silicone film deforms into a convexed dome-like shape as shown by a numeral 245 when there is a flow of air. The operator is able to see if there is a certain amount of air to be discharged according to a shape of the silicone film. In Fig. 14, a float 243 having a rather flat triangular pyramid shape moves by the air flowing toward it from the check valve. The operator is able to see if there is a certain amount of air to be discharged by observing a movement of the float 243.

The efficiency value of C1/C2 is important for the vacuum pump of this invention. An internal pressure of 30torr or lower in the cylinder can be attained when the formula of C1/C2 ≥ 40 is satisfied in designing. Furthermore, the formula of C1/C2 ≥ 40 is necessary in order to assure reliability of the refrigeration cycle for an extended period of time. If the value of C1/C2 is too large, it gives rise to a problem in workability, although it makes no difficulty in gaining a degree of vacuum.

The vacuum pump of this invention is provided with a double seal for the piston shaft, using double O-ring or a gourd-shaped ring made of elastomer having approximately 60 to 90 in hardness as measured by a spring type instrument of A-type (Japanese Industrial Standard K6301), such as HNBR (Hydrogenated nitrile-butadiene rubber), CR (Chloroprene rubber), EPDM (Ethylene propylene-diene), NBR (Nitrile-butadiene rubber), and the like. An outside seal of the double seal fulfills the function of removing dust that adheres to the piston shaft when the piston shaft travels outside of the cylinder. In addition, the double seal can maintain air-tightness with any one of the seals even if air leakage occurs through another of the seals due to an abrupt movement of the piston shaft.

As an alternate structure of the check valves, a light-weight small metallic ball movably placed in a pipe may be used to construct a closing valve structure. In addition, such resins as nylon, fluorine series resins like PFA (Perfluoro-alkoxy-fluoro plastics) and PVDF (Polyvinylidene fluoride), PPS (Polyphenylene sulfide), and the like may also be suitable to use for the check valves. It is desirable that the check valve for the inlet port is capable of blocking airflow with a difference in pressure as small as 10torr or less, and more desirably 1torr or less, since there decreases the difference between an internal pressure of the indoor unit and the connecting tubes, and an internal pressure of the cylinder, as the piston is continued to operate. In addition, it is also desirable to keep 1 ml/min or less the amount of gas leakage under the condition of 1 kgf/cm² in the difference of pressure. The reason for this is to avoid a rapid decrease in degree of vacuum theretofore attained, just as the operator stops operating the piston.

The piston of the vacuum pump is adaptable for operation with a foot treadle, although the piston in the above exemplary embodiments is illustrated as being operable with hand. When the earth environment is considered, this provides an advantageous effect to reduction of the environmental burden during installation of the air conditioner, because the satisfactory level of vacuum is attainable with human power using the handlebar or the treadle, as opposed to the conventional motor-driven pump.

Claims

A vacuum pump comprising:

a cylinder provided with a top end plate covering a top end of said cylinder and a bottom end plate covering a bottom end of said cylinder;

a piston for reciprocating between a top position and a bottom position in said cylinder, said piston having an upper surface and a lower surface, and dividing an interior of said cylinder into two chambers;

a piston shaft connected to the upper surface of said piston, said piston shaft protruding outwardly from said cylinder through the top end plate of said cylinder;

a suction check valve disposed to the top end plate of said cylinder, for allowing suction air to said cylinder pass through, but not allowing discharge air from said cylinder pass though;

a discharge check valve disposed to the top end plate of said cylinder, for allowing discharge air from said cylinder pass though, but not allowing suction air to said cylinder pass through;

a suction check valve disposed to the bottom end plate of said cylinder, for allowing suction air to said cylinder pass through, but not allowing discharge air from said cylinder pass though; and

a discharge check valve disposed to the bottom end plate of said cylinder, for allowing discharge air from said cylinder pass though, but not allowing suction air to said cylinder pass through,

wherein an upper chamber and a lower chamber in said cylinder alternately suction air from a subject of suctioning through said suction check valve on the top end plate and said suction check valve on the bottom end plate, and discharge the suctioned air to the outer space through said discharge check valve on the top end plate and said discharge check valve on the bottom end plate, in synchronization with the reciprocatory movement of said piston.
The vacuum pump as set forth in claim 1 having a structure satisfying a formula, which is C1/C2 ≥ 40, where

C1 represents a capacity bounded from the lower surface of said piston to said suction check valve and said discharge check valve disposed to the bottom end plate of said cylinder when said piston is at the top position, and

C2 represents a capacity bounded from the lower surface of said piston to said suction check valve and said discharge check valve disposed to the bottom end plate of said cylinder when said piston is at the bottom position.
The vacuum pump as set forth in any of claim 1 and claim 2, wherein an airflow passage to said suction check valve disposed to the top end plate of said cylinder and another airflow passage to said suction check valve disposed to the bottom end plate of said cylinder are connected together into one airflow passage outside said cylinder.
The vacuum pump as set forth in any one of claim 1 through claim 3 further having a handlebar attached to a top end of said piston shaft protruding outwardly from said cylinder for manual operation.
The vacuum pump as set forth in any one of claim 1 through claim 4 further having filters, each of said filters connected detachably to a hose comprising the airflow passage to said suction check valve disposed to the top end plate of said cylinder, and another hose comprising the airflow passage to said suction check valve disposed to the bottom end plate of said cylinder.
The vacuum pump as set forth in claim 5, wherein said filter has a transparent container.
The vacuum pump as set forth in any one of claim 1 through claim 6 further having an airflow detector connected to at least one of said discharge check valve disposed to the top end plate of said cylinder and said discharge check valve disposed to the bottom end plate of said cylinder.
The vacuum pump as set forth in claim 7, wherein said airflow detector is provided with a film or a movable element moved by the airflow.
The vacuum pump as set forth in any one of claim 1 through claim 8 further comprising a shaft seal disposed to a part of the top end plate of said cylinder where said piston shaft passes through.
The vacuum pump as set forth in claim 9, wherein said shaft seal is formed of elastomer, and seals said piston shaft at least double.
The vacuum pump as set forth in any one of claim 1 through claim 10 wherein a minimum operable pressure difference of said suction check valve is 10torr or less.
The vacuum pump as set forth in claim 11, wherein said suction check valve has a structure comprising a thin plate made of resin film and a spring for blocking the airflow when said thin plate is thrust against the airflow passage with said spring.
The vacuum pump as set forth in claim 12, wherein said airflow passage is tapered in an upstream side of a point where the airflow is blocked.