JP2005240724A - Refrigerant conveying pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a suitable refrigerant conveying pump used in a secondary side cycle in which a refrigerant is thermally conveyed as sensible heat in a supercritical state during a heating period and as latent heat at the time of phase change during a cooling period. <P>SOLUTION: This refrigerant conveying pump 1 is used in the secondary side cycle 7 in which the refrigerant is thermally conveyed as sensible heat in the supercritical state during the heating period and as latent heat at the time of phase change during the cooling period. The refrigerant conveying pump 1 has a first piston 49 and a second piston 50 on the both ends, respectively, and is provided with a first cylinder part 63 slidably supporting a shaft 47 capable of reciprocating in a piston connection axial direction and the pistons 49, 40 from the outer side, a first compression chamber 81 formed between the first piston 49 and the first cylinder part 63 and communicated with a suction hole 65 and a first discharge hole 63, and a drive means 45 reciprocating a shaft 47 in the axial direction. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a refrigerant transfer pump suitable for use in an air conditioner that pressurizes a refrigerant to a supercritical region and encloses the refrigerant in a secondary cycle and circulates the refrigerant to perform an air conditioning operation. .

  The refrigerant is pressurized to the supercritical region and sealed in the secondary cycle (also referred to as “indoor cycle” or “use cycle”), and the refrigerant is circulated in the secondary cycle to perform the air conditioning operation. As an air conditioner, there exists a thing shown in patent document 1, for example.

JP-A-9-79694 (paragraphs [0037] to [0040] and FIG. 5)

  By the way, Patent Document 1 does not describe any specific structure of the refrigerant conveyance pump used in the secondary side cycle, and serves as a refrigerant conveyance pump for pumping the refrigerant pressurized to the supercritical region. The desired structure was not known.

  In view of the above circumstances, the present invention provides a refrigerant transfer pump suitable for use in a secondary cycle in which heat is transferred as sensible heat in a supercritical state during heating and is transferred as latent heat during phase change during cooling. For the purpose.

In order to solve the above problems, the present invention employs the following means.
That is, the refrigerant transfer pump according to the present invention is a refrigerant transfer pump used for a secondary cycle that is heat-transferred as sensible heat in a supercritical state during heating, and heat-transferred as latent heat at the time of phase change during cooling. Each end has a piston, a shaft provided so as to be able to reciprocate in the direction of the piston connection axis, a cylinder portion that supports each piston so as to be slidable from the outside, and between the piston and the cylinder portion A compression chamber that is formed and communicated with the suction portion and the discharge portion, and a drive unit that reciprocally drives the shaft in the axial direction are provided.

According to such a refrigerant transport pump, when the shaft is driven to one side by the driving means, the refrigerant is discharged from the compression chamber on one side via the discharge unit, and at the same time, the refrigerant is discharged to the compression chamber on the other side. Inhaled. When the shaft is driven in the opposite direction by the driving means, contrary to the above, the refrigerant is discharged from the compression chamber on the other side and simultaneously sucked into one compression chamber. By repeating this, the refrigerant is continuously sucked into the refrigerant transfer pump and continuously discharged.
As described above, when the suction and discharge of the refrigerant are continuously performed, a large load at the time of constant discharge and a small load at the time of suction are applied, so that fluctuations in driving force can be reduced. In addition, since the refrigerant is always supplied in the secondary cycle in a state where the required amount is continuously, that is, the difference between the portion with a large supply amount and the portion with a small supply amount (small pulsation), Heat exchange can be performed stably.
For example, if the area of the piston and the stroke are the same, the suction volume is twice that in the case of a single compression chamber. If the refrigerant suction amount is the same, the refrigerant suction speed, that is, the suction amount per unit time, is half that of a single compression chamber. Thus, when the suction speed of the refrigerant is reduced, pressure loss caused by factors such as friction and flow path resistance when the refrigerant is sucked can be reduced. Therefore, since the pressure loss when the refrigerant is sucked can be reduced, for example, in the cooling operation in which heat is transferred as latent heat at the time of phase change, the pressure in the compression chamber decreases and the liquid and gas are separated into two layers. It is possible to prevent a situation in which compression is not possible.

  Moreover, the refrigerant | coolant conveyance pump concerning this invention attaches a tubular member between each said cylinder parts so that the said shaft may be covered, employ | adopts a linear motor as the said drive means, and the drive part of the said linear motor outside the said tubular member Is provided.

As described above, the linear motor is employed as the driving means, and the linear motor driving portion is provided outside the tubular member. Therefore, the rotating portion can be eliminated in the space formed by the cylinder portion and the tubular member. . For this reason, the refrigerant transfer pump does not require sufficient lubrication, so even if there is a state in which the lubricating oil cannot be transferred due to the density difference like the refrigerant transferred in the supercritical state during heating operation, the refrigerant transfer pump functions. It does not affect. Therefore, the refrigerant conveyance pump can perform stable operation over a long period of time.
Further, since the tubular member is attached to the cylinder portion so as to cover the shaft, a sealed space is formed by the cylinder portion and the tubular member. For this reason, since the refrigerant leaking from the seal between the cylinder part and the piston is prevented from leaking outside by the tubular member, it can be operated for a long time without replenishing the refrigerant and adversely affect the surrounding environment. Can be prevented.
Furthermore, since there is no rotating part in the space formed by the cylinder part and the tubular member, the sectional shape of the tubular member can be any shape such as a circle, a polygon, and a closed shape composed of straight lines and curves. It can be.

Furthermore, in the refrigerant transport pump according to the present invention, the tubular member is made of a non-magnetic material.
Thus, since the tubular member is made of a non-magnetic material, it does not affect the magnetic field generated by the linear motor or the like. Therefore, the driving efficiency of the linear motor can be improved.

  Further, in the refrigerant transport pump according to the present invention, the shaft is configured by a plurality of rod-shaped members that connect the pistons at both ends, and the tubular member is provided so as to cover the rod-shaped members. It is characterized by.

Thus, since the shaft is composed of a plurality of rod-shaped members that connect the pistons at both ends, the cross-sectional area of each rod-shaped member is reduced. When the cross-sectional area of the rod-like member is reduced, the cross-sectional area of the tubular member covering the rod-like member can be reduced, so that the pressure resistance of the tubular member is improved and the tubular member can be thinned. Therefore, since the drive part of the linear motor provided in the outer side of the tubular member can be disposed close to the rod-like member, the drive force of the linear motor can be increased.
In addition, it is possible to optimally arrange a comprehensive magnetic circuit, and to improve driving efficiency.
In addition, it is desirable from the viewpoint of driving balance that the rod-like members are arranged at equal intervals on the same circumference. Further, the number is preferably 3 or more, and more preferably a point-symmetrical positional relationship such as four.

  In the refrigerant transport pump according to the present invention, a sleeve is attached to the cylinder portion so as to cover the tubular member from the outside, and a hole formed through the sleeve in the thickness direction is provided in the sleeve. The operation part which comprises the drive part of the said linear motor is arrange | positioned in the hole part, It is characterized by the above-mentioned.

Thus, since the sleeve is attached to the cylinder portion so as to cover the tubular member from the outside, the sleeve reinforces the strength of the tubular member. For this reason, since a tubular member does not require high intensity | strength in spite of receiving high pressure called a supercritical pressure, thickness can be made thin.
Accordingly, since the distance between the action part constituting the drive part of the linear motor arranged in the hole provided in the sleeve and the driven part of the linear motor attached to the shaft is shortened, the action part is driven. The magnetic force given to the part becomes stronger. For this reason, the driving force of the linear motor can be increased and the size can be reduced.
In the case where the tubular member and the sleeve are made of the same material, it is desirable that a gap of several microns to several tens of microns be provided between the tubular member and the sleeve at the time of assembly because of easy processing and assembly. In the case of dissimilar materials, it is desirable that the gap is a gap that takes into account the thermal deformation due to the difference between the assembly temperature and the use temperature.

In the refrigerant transport pump according to the present invention, the sleeve is made of a nonmagnetic material.
Thus, since the sleeve is made of a non-magnetic material, it does not affect the magnetic field generated by the linear motor or the like. Therefore, the driving efficiency of the linear motor can be improved.

  Further, in the refrigerant transport pump according to the present invention, the drive unit of the linear motor is connected to a general-purpose motor, a crank that is connected to a rotary shaft of the general-purpose motor, and converts the rotation of the rotary shaft into a reciprocating motion, and a tip of the crank And a permanent magnet attached to the head.

Thus, since the drive part of a linear motor is mainly comprised by the general purpose motor, the crank which converts rotation into reciprocating motion, and a permanent magnet, each component is cheap and can be manufactured cheaply as a whole. Maintenance can also be easily performed.
In addition, since a permanent magnet is employed as the action part, the generation of eddy current due to the magnetic field fluctuation is reduced. For this reason, restrictions on the materials used for the peripheral members are relaxed, and the degree of freedom in design can be increased.

  Furthermore, the refrigerant transfer pump according to the present invention is characterized in that a protrusion is provided at a middle position in the sliding direction on the side surface of the piston so that a gap with the cylinder portion is narrower than both ends in the sliding direction. And

  In this way, since the protrusion with a narrow gap between the cylinder part and the cylinder part is provided at the intermediate position in the sliding direction on the side surface of the piston, the piston slides relative to the cylinder part. The dynamic pressure of the refrigerant that has entered the gap between the end of the cylinder and the cylinder portion increases at the projection where the gap is narrow. For this reason, since the force which tries to keep a piston away from a cylinder part increases, it can prevent that a piston contacts a cylinder part.

According to the first aspect of the present invention, since the pistons are provided at both ends of the reciprocating shaft, the refrigerant is continuously sucked into the refrigerant transfer pump and continuously discharged. . For this reason, the heat exchange in a secondary side cycle can be performed stably.
In addition, since the suction volume is increased and the pressure loss when the refrigerant is sucked can be reduced, for example, in the cooling operation in which heat is transferred as latent heat at the time of phase change, the pressure in the compression chamber decreases, and the liquid and gas It is possible to prevent a situation in which the two layers cannot be compressed after being separated.

According to the second aspect of the present invention, since the linear motor is employed as the driving means and the linear motor driving portion is provided outside the tubular member, the refrigerant transport pump performs stable operation over a long period of time. be able to.
Further, since the tubular member is attached to the cylinder portion so as to cover the shaft, it can be operated for a long time without replenishing the refrigerant, and adverse effects on the surrounding environment can be prevented.

  According to the invention described in claim 3, since the tubular member is made of a non-magnetic material, the drive efficiency of the linear motor can be improved.

  According to invention of Claim 4, since the shaft is comprised by the several rod-shaped member which connects between the said pistons of both ends, respectively, the tubular member which covers a rod-shaped member can be made thin. Therefore, the driving force of the linear motor can be increased.

According to the fifth aspect of the present invention, since the sleeve is attached to the cylinder portion so as to cover the tubular member from the outside, the thickness of the tubular member can be reduced.
Accordingly, the distance between the action part constituting the driving part of the linear motor and the driven part of the linear motor attached to the shaft is shortened, so that the driving force of the linear motor can be increased and the size can be reduced.

  According to the sixth aspect of the invention, since the sleeve is made of a nonmagnetic material, the drive efficiency of the linear motor can be improved.

  According to the invention described in claim 7, since the drive unit of the linear motor is mainly composed of a general-purpose motor, a crank that converts rotation into a reciprocating motion, and a permanent magnet, each component is inexpensive, As a whole, it can be manufactured at low cost, and maintenance can be easily performed.

  According to the eighth aspect of the present invention, since the protrusion is provided at the intermediate position in the sliding direction on the side surface of the piston so that the gap with the cylinder is narrower than the both ends in the sliding direction. It is possible to prevent contact with the part.

Embodiments according to the present invention will be described below with reference to the drawings.
[First embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a schematic configuration diagram showing an air conditioner 3 using a refrigerant transfer pump 1 according to the present embodiment.
The air conditioner 3 includes a primary side cycle 5 and a secondary side cycle 7.

The primary side cycle 5 includes a compressor 9, a four-way valve 11, an outdoor heat exchanger 13, an expansion valve 15, an inter-refrigerant heat exchanger 17, an intake gas heater 19, and a primary side pipe 21. Is provided.
The compressor 9 sucks and compresses a low-temperature / low-pressure gaseous refrigerant (as a refrigerant, for example, a hydrocarbon refrigerant such as propane, butane, and isobutane (a refrigerant containing carbon (C) and hydrogen (H)). This is a high-temperature, high-pressure gaseous refrigerant.

  The four-way valve 11 is provided on the downstream side of the compressor 9 and switches the flow path of the refrigerant discharged from the compressor 9 between the cooling operation and the heating operation. The four-way valve 11 forms a flow path from the compressor 9 toward the inter-refrigerant heat exchanger 17 during the heating operation (when the refrigerant is circulated in the direction indicated by the solid line arrow in FIG. 1), while the cooling operation is performed. When the refrigerant is circulated in the direction indicated by the broken-line arrow in FIG. 1, a flow path from the compressor 9 toward the outdoor heat exchanger 13 is formed.

The outdoor heat exchanger 13 functions as a condenser that condenses and liquefies high-temperature and high-pressure gaseous refrigerant during cooling operation and dissipates heat to the outside air, and conversely evaporates low-temperature and low-pressure liquid refrigerant during heating operation and takes heat from the outside air. It functions as an evaporator.
The expansion valve 15 decompresses and expands the refrigerant passing through the interior in an enthalpy manner to form a low-temperature and low-pressure refrigerant.

  The inter-refrigerant heat exchanger 17 exchanges heat between the refrigerant circulating in the primary cycle 5 and the refrigerant circulating in the secondary cycle 7. The inter-refrigerant heat exchanger 17 heats the refrigerant that circulates in the secondary side cycle 7 by the refrigerant that circulates in the primary side cycle 5 during heating operation, and the secondary side by the refrigerant that circulates in the primary side cycle 5 during cooling operation. The refrigerant circulating in the cycle 7 is cooled.

In addition, a temperature sensor T is provided in the pipe 21 located in the vicinity of the inlet of the primary cycle 5 of the inter-refrigerant heat exchanger 17, and the refrigerant temperature data in the pipe 21 detected by the temperature sensor T is controlled. Is output to the device 25.
The intake gas heater 19 is a heat exchanger provided on the upstream side of the compressor 9 (that is, between the compressor 9 and the four-way valve 11), and exits the inter-refrigerant heat exchanger 17 during heating operation. The warm refrigerant cools the refrigerant before being sucked into the compressor 9 and increases the temperature of the refrigerant before being sucked into the compressor 9.

The primary side pipe 21 connects the compressor 9, the four-way valve 11, the outdoor heat exchanger 13, the expansion valve 15, the inter-refrigerant heat exchanger 17, and the suction gas heater 19, and refrigerant is connected between these components. It is intended to be able to circulate.
Further, the bypass pipe 23 is connected to the primary side pipe 21, and the refrigerant that has exited the inter-refrigerant heat exchanger 17 does not pass through the intake gas heater 19 during the heating operation, and is downstream of the intake gas heater 19. It is led directly to the upstream side of the expansion valve 15 located at the position.

  Flow rate control valves 27 and 29 are provided in the primary pipe 21 and the bypass pipe 23 downstream of the bypass pipe 23 and upstream of the intake gas heater 19, respectively. Each of these flow rate adjusting valves 27 and 29 is configured so that the valve opening is adjusted by a signal from the controller 25, and the amount of refrigerant flowing from the inter-refrigerant heat exchanger 17 into the suction gas heater 19, and The amount of refrigerant flowing into the expansion valve 15 from the inter-refrigerant heat exchanger 17 is adjusted. The amount of refrigerant flowing from the inter-refrigerant heat exchanger 17 to the intake gas heater 19 and the amount of refrigerant flowing from the inter-refrigerant heat exchanger 17 to the expansion valve 15 are adjusted.

The secondary side cycle 7 includes the inter-refrigerant heat exchanger 17, the refrigerant transfer pump 1, the indoor heat exchanger 31, the secondary side pipe 33, and the flow rate adjustment valve 35.
The refrigerant transfer pump 1 will be described in detail later. The refrigerant transfer pump 1 circulates a refrigerant (for example, carbon dioxide) pressurized to the supercritical region (for example, carbon dioxide) in the secondary cycle 7.

The indoor heat exchanger 31 exchanges heat between the refrigerant passing through the interior and the air blown into the room, and functions as a so-called evaporator during cooling operation and as a so-called condenser during heating operation.
The secondary side pipe 33 connects the inter-refrigerant heat exchanger 17, the indoor heat exchanger 31, and the refrigerant transport pump 1, and allows the refrigerant to circulate between these components.
The flow rate adjusting valve 35 is provided in the secondary side pipe 33 positioned on the upstream side of each indoor heat exchanger 31, and the amount of refrigerant flowing from the inter-refrigerant heat exchanger 17 into the indoor heat exchanger 31 is adjusted. It is like that.

The refrigerant transfer pump 1 according to the embodiment of the present invention will be described with reference to FIG.
The refrigerant transfer pump 1 is provided with a piston member 41, a cylinder 43, and a driving unit 45 that drives the piston member 41.
The piston member 41 includes a shaft 47, a first piston 49 fixed to one end portion 46 of the shaft 47, and a second piston 50 fixed to the other end portion 48 of the shaft 47.
The shaft 47 is an elongated cylindrical rod, and is formed with a groove 53 that is inclined near the center in the longitudinal direction and is continuous over the entire circumference.

  The first piston 49 has a hollow, substantially cylindrical shape that is coaxial with the shaft 47. A bottom surface portion 51 of the first piston 49 is fixed to one end portion 46 of the shaft 47, and a plurality of through holes 55 are provided at intervals on a circle coaxial with the shaft 47. A through hole 59 is provided at the center of the outer portion 57 of the first piston 49. A first suction valve 61 that covers the through hole 59 is provided outside the outer portion 57.

  The second piston 50 has the same structure as the first piston 49. The bottom surface portion 52 fixed to the other end portion 48 of the shaft 47 is provided with a large number of through holes 56 at intervals on a circle coaxial with the shaft 47. A through hole 60 is provided at the center of the outer portion 58 of the second piston 50. A second suction valve 62 that covers the through hole 60 is provided outside the outer portion 58.

The cylinder 43 includes a first cylinder part (cylinder part) 63, a second cylinder part (cylinder part) 64, and a can (tubular member) 65.
The first cylinder body 65 of the first cylinder portion 63 has an outer flange 67 and an inner flange 69 at both ends, and has a substantially cylindrical shape coaxial with the shaft 47. An inner surface 83 of the first cylinder body 65 is fitted to a side surface 85 of the first piston 49 to support the first piston 49 so as to be slidable.

As shown in FIG. 3, the side surface 85 of the first piston is provided with a protrusion 103 so that the diameter is sequentially increased from the one end side end portion 105 and the other end side end portion 107 toward the intermediate position in the sliding direction. Yes.
In this case, for example, when the first piston 49 slides toward the one end, the refrigerant enters between the one end 105 and the inner peripheral surface 83 of the cylinder 65 and moves in the direction of the protrusion 103. Since the interval is narrowed, the dynamic pressure increases. It becomes maximum at the protrusion 103. Since the first piston 49 is supported by this dynamic pressure, it does not contact the inner peripheral surface 83 of the cylinder 65. This dynamic pressure also produces a sealing effect.
The difference C between the radius of the one end 105 and the other end 107 and the radius of the protrusion 103 is 1 when the distance between the protrusion 103 and the inner surface 65 of the first cylinder body 65 is δ. ˜5 times is preferred.

A first lid member 71 is fixed to the outer flange 67 of the first cylinder body 65. A first valve member 73 is attached to the center of the first lid member 71, and the opening of the first cylinder body 65 is sealed by the first lid member 71 and the first valve member 71. A first compression chamber 81 surrounded by the inner surface 83 of the first cylinder body 65 and the outer portion 57 of the first piston 49 is formed.
The first valve member 71 has a donut-shaped discharge space 87 having an opening 89 facing the first compression chamber 81, and a donut-shaped first discharge hole communicating the discharge space 87 and the secondary side pipe 33. 75 and a hollow disc-shaped first discharge valve 77 which is disposed inside the discharge space 87 and covers the opening 89 is provided.

The second cylinder part 64 has substantially the same structure as the first cylinder part 63. The second cylinder body 66 has an outer flange 68 and an inner flange 70 at both ends, and has a substantially cylindrical shape coaxial with the shaft 47. The inner surface 84 of the second cylinder body 66 is fitted to the side surface 86 of the second piston 50 to support the second piston 50 so as to be slidable.
In addition, the protrusion part 103 is provided in the side surface 86 of the 2nd piston 50 similarly to the side surface 85 of the above-mentioned 1st piston 49. FIG.

A second lid member 72 is fixed to the outer flange 68 of the second cylinder body 66. A second valve member 74 is attached to the center of the second lid member 72, and the opening of the second cylinder body 66 is sealed by the second lid member 72 and the second valve member 72. The second compression chamber 82 surrounded by the inner surface 84 of the second cylinder body 66 and the outer portion 58 of the second piston 50 is formed.
The second valve member 72 includes a donut-shaped discharge space 88 having an opening 90 facing the second compression chamber 82, a donut-shaped second discharge hole 76 that connects the discharge space 88 and the outside, and a discharge A hollow disc-shaped second discharge valve 78 that is disposed inside the empty space 88 and covers the opening 90 is provided.

The can 92 has a thin cylindrical shape, and is arranged so as to cover the shaft 47 with a space therebetween. The can 92 is made of a nonmagnetic material such as stainless steel or invar.
Both ends of the can 92 are attached to a support member 79 and a support member 80. Since the support member 79 is fixed to the inner flange 69 of the first cylinder main body 65 and the support member 80 is fixed to the inner flange 70 of the second cylinder main body 66, the can 92 is connected to the first cylinder portion 63. The first cylinder portion 63, the second cylinder portion 64, and the can 92 form a sealed space.
A suction hole 93 that communicates the suction space 91 defined by the first piston 49 and the second piston 50 and the secondary pipe 33 is provided on the inner side of the first cylinder body 65. .

The driving means 45 is provided with a stator core 95, a stator winding 97, and a rotor 99.
The stator core 95 and the stator winding 97 are fixedly disposed outside the can 92. The stator core 95 also functions to prevent the can 92 from being deformed or broken by the high pressure of the suction space 91.
The rotor 99 is disposed between the can 92 and the shaft 47 and is rotatably supported by the first cylinder body 65 and the second cylinder body 66. On the shaft 47 side of the rotor 99, a protrusion 101 that engages with a groove 53 provided in the shaft 47 is provided.
The protrusion 101 moves along the groove 53 by the rotation of the rotor 99. However, since the axial position of the shaft 47 of the protrusion 101 is constant, the groove 53 moves in the axial direction, that is, the shaft 47 moves in the axial direction. Become. Since the groove 53 is inclined and continuous over the entire circumference, the shaft 47 reciprocates once when the rotor 99 makes one revolution. That is, the groove 53 and the protrusion 101 function as a cylindrical cam.

Operation | movement of the refrigerant | coolant conveyance pump 1 concerning this embodiment demonstrated above is demonstrated.
The refrigerant transfer pump 1 handles a refrigerant that is heat-transferred as sensible heat in a supercritical state during heating and is heat-transferred as latent heat during phase change during cooling. When carbon dioxide is used as the refrigerant, it is conveyed with a pressure of about 10 MPa during heating and about 4 MPa during cooling, for example. The refrigerant transport pump 1 sucks the refrigerant transported in the secondary side pipe 33 of the secondary side cycle 7 with such a pressure, raises the pressure by about 0.3 to 0.5 MPa, and discharges it. .

When the stator winding 97 is energized, a rotating magnetic field is generated and the rotor 99 rotates. The groove 53 is pulled by the protrusion 101 by the rotation of the rotor 99, and the shaft 47 reciprocates in the axial direction.
In FIG. 2, the first piston 49 moves to one end side (left side in FIG. 2), and the refrigerant sucked into the first compression chamber 81 by the first piston 49 passes through the first discharge hole 75 to the secondary side. The state discharged to the secondary side pipe 33 of the cycle 7 is shown.

When the rotor 99 further rotates from the state of FIG. 2, the shaft 47 starts to move to the other end side (right side in FIG. 2). The second suction valve 62 covering the through hole 60 of the second piston 50 is closed, and the first suction valve 61 covering the through hole 59 of the first piston 49 is opened.
When the first piston 49 moves to the other side with the first suction valve 61 open, the refrigerant sucked into the suction space 91 passes through the through hole 55, the hollow portion of the first piston 49, and the through hole 51. It is sucked into the first compression chamber 81 through. By being sucked into the first compression chamber 81, the refrigerant in the secondary side pipe 33 is sucked into the suction space 91 through the suction hole 93.

On the other hand, since the second piston 50 is moved to the other side with the second suction valve 62 closed at the same time, the refrigerant sucked into the second compression chamber 82 is pressed by the second piston 50 and the opening portion The second discharge valve 78 is pushed up from 90 and introduced into the discharge space 88, and continuously discharged from the second discharge hole 76 to the secondary side pipe 33 of the secondary side cycle 7.
Thus, since the refrigerant in the second compression chamber 82 is pressed in a state in which the second suction valve 62 is closed, that is, in a state in which the second piston 50 side of the second compression chamber 82 is closed, the inertia resistance of the refrigerant The effect of this is almost eliminated and the refrigerant can be discharged smoothly.

Then, at the timing when the second piston 50 reaches the other end side, the rotor 99 starts to move the shaft 47 to the one end side. Then, the operation opposite to that described above is performed.
That is, the first suction valve 61 covering the through hole 59 of the first piston 49 is closed, and the second suction valve 62 covering the through hole 60 of the second piston 50 is opened.
When the second piston 50 moves to the other side with the second suction valve 62 opened, the refrigerant sucked into the suction space 91 passes through the through hole 56, the hollow portion of the second piston 50, and the through hole 52. It is sucked into the second compression chamber 82 through. By being sucked into the second compression chamber 82, the refrigerant in the secondary side pipe 33 is sucked into the suction space 91 through the suction hole 93.

  On the other hand, since the first piston 49 is moved to the other side while the first suction valve 61 is closed at the same time, the refrigerant sucked into the first compression chamber 82 is pressed by the first piston 49 and is opened. The first discharge valve 77 is pushed up from 89 and introduced into the discharge space 87, and discharged continuously from the first discharge hole 75 to the secondary side pipe 33 of the secondary side cycle 7.

  By the rotation of the rotor 99, the above-described operation is repeated, and the refrigerant is continuously and continuously supplied from the first discharge hole 75 and the second discharge hole 76 to the secondary side pipe 33 of the secondary side cycle 7. Discharged. Therefore, since the discharge amount to the secondary side pipe 33 is always substantially constant, the refrigerant conveyed through the secondary side pipe 33 does not periodically increase and decrease. Thereby, since the refrigerant flowing through the indoor heat exchanger 31 does not pulsate, heat exchange can be performed stably.

  Further, in both cases, when the shaft 47 moves to one end side and to the other end side, both the discharge load and the suction load are applied to the shaft 47, so that the driving force There is little fluctuation and the operation can be balanced.

Further, in the cooling operation, in the case of cooling the indoor air with the heat of evaporation when the refrigerant conveyed in the liquid state changes into a gas, the refrigerant under the condition that the phase easily changes is conveyed. For this reason, if the pressure loss at the time of suction by the refrigerant transport pump 1 is large, the liquid and gas may be separated into two layers and cannot be compressed at the time of suction.
In the present embodiment, since either one of the first compression chamber 81 and the second compression chamber 82 is always sucking, the refrigerant is used when the same suction amount is maintained as compared with intermittent suction. The inhalation speed will decrease. If the suction speed of the refrigerant decreases, pressure loss caused by friction, flow path resistance, etc. can be reduced when the refrigerant is sucked, so that the liquid and gas cannot be separated into two layers and compressed as described above. Can be prevented.

Note that the side surface 85 of the first piston 49 and the side surface 86 of the second piston 50 according to the present embodiment are provided with a protruding portion 103 shaped so as to gradually increase toward the center position as shown in FIG. However, the shape of the protrusion 103 is not limited to this.
For example, as shown in FIG. 4, the diameter may be a step shape. In the case of FIG. 4, the number of stages is one, but it may be changed to a plurality of stages.
Even in this case, the difference C between the radius of the one end side end portion 105 and the other end side end portion 107 and the radius of the projection portion 103 is when the interval between the projection portion 103 and the inner surface 65 of the first cylinder body 65 is δ. 1 to 5 times δ is preferable.

Moreover, when improving a sealing effect, as shown in FIG. 5, you may employ | adopt the structure which reduces a diameter toward a pumping direction (discharge direction).
Furthermore, as shown in FIG. 6, when a large number of fine grooves are provided on the side surface 85 of the first piston 49 and the side surface 86 of the second piston 50 in a direction perpendicular to the traveling direction of the first piston 49 and the second piston 50. The labyrinth seal effect reduces refrigerant leakage and improves pump efficiency.

Hereinafter, the operation and effect of this embodiment will be described.
According to the refrigerant transfer pump 1 according to the present embodiment, when the shaft 47 is driven to one side by the driving unit 45, the refrigerant is discharged from the first compression chamber 81 on one side via the discharge hole 75, At the same time, the refrigerant is sucked into the second compression chamber 82 on the other side. When the shaft 47 is driven in the opposite direction by the driving means 45, the refrigerant is discharged from the second compression chamber 82 on the other side and sucked into the first compression chamber 81 at the same time, contrary to the above. By repeating this, the refrigerant is continuously sucked into the refrigerant transfer pump 1 and continuously discharged.
As described above, when the suction and discharge of the refrigerant are continuously performed, a large load at the time of constant discharge and a small load at the time of suction are applied, so that fluctuations in driving force can be reduced. In addition, the refrigerant is always supplied to the secondary side pipe 33 of the secondary side cycle 7 in a state where the required amount is continuously, that is, in a state where the difference between the part with a large supply amount and the part with a small supply amount is small (pulsation is small) Heat exchange in the secondary cycle 7 can be performed stably.
Further, for example, if the area of the piston and the stroke are the same, the suction volume of the compression chamber is twice that of a single pump. If the suction amount of the refrigerant is the same, the suction speed of the refrigerant, that is, the suction amount per unit time is half that of a pump with one compression chamber. Thus, when the suction speed of the refrigerant is reduced, pressure loss caused by factors such as friction and flow path resistance when the refrigerant is sucked can be reduced. Therefore, since the pressure loss when the refrigerant is sucked can be reduced, for example, in the cooling operation in which heat is transferred as latent heat at the time of phase change, the pressure in the compression chamber decreases and the liquid and gas are separated into two layers. It is possible to prevent a situation in which compression is not possible.

  In addition, a gap between the inner surface 83 of the first cylinder main body 65 and the inner surface 84 of the second cylinder main body 66 is located at one end side at an intermediate position in the sliding direction between the side surface 85 of the first piston 49 and the side surface 86 of the second piston 50. Since the protrusion 103 is provided so as to be narrower than the end 105 and the other end 107, the first piston 49 and the second piston 50 are connected to the inner surface 83 of the first cylinder body 65 and the inner surface of the second cylinder body 66. 84 can be prevented from touching.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
Since the air conditioner 3 using the refrigerant transport pump 1 according to the present embodiment is the same as that described in the first embodiment, the description thereof is omitted.
The refrigerant transfer pump 1 is provided with a piston member 103, a cylinder 105, and a driving means 107 that drives the piston member 103.
The piston member 103 includes a shaft 109, a first piston 113 fixed to one end portion 111 of the shaft 109, and a second piston 114 fixed to the other end portion 112 of the shaft 109.

The shaft 109 has a double cylindrical shape having a large diameter portion 115 at the center.
The first piston 113 has a substantially cylindrical shape in which a reduced diameter portion 117 is provided at a tip having a coaxial center with the shaft 109. A bottom surface portion 119 of the first piston 113 is fixed to one end portion 111 of the shaft 109.
The second piston 114 has a substantially cylindrical shape in which a reduced diameter portion 118 is provided at a tip having a coaxial center with the shaft 109. The bottom surface 120 of the second piston 114 is fixed to the other end 112 of the shaft 109.

The cylinder 105 includes a first cylinder part (cylinder part) 121, a second cylinder part (cylinder part) 122, and a can (tubular member) 123.
The first cylinder body 125 of the first cylinder part 121 has an inner flange 133 at the inner end, and has a substantially cylindrical shape coaxial with the shaft 109. An inner surface 127 of the first cylinder body 125 is fitted with a side surface 129 of the first piston 113 to support the first piston 113 so as to be slidable. Seal members 131 and 131 are provided on the side surface 129 of the first piston 113.

A first lid member 135 is fixed to the outside of the first cylinder body 125. A first suction space 141 and a first discharge space 145 are formed on the inner surface of the first lid member 135. The first suction space 141 communicates with the secondary side pipe 33 of the secondary side cycle 7 through the first suction hole 143. The first discharge space 145 communicates with the secondary side pipe 33 of the secondary side cycle 7 through the first discharge hole 147.
A first valve member 137 is attached between the first cylinder body 125 and the first lid member, and the first lid member 135 and the first valve member 137 allow the first cylinder body 125 to open to the outside. Is sealed. A first compression chamber 139 is formed that is surrounded by the first lid member 135, the first valve member 137, the inner surface 127 of the first cylinder body 125, and the reduced diameter portion 117 of the first piston 113.
The first valve member 137 is provided with a discharge hole 149 that allows the first compression chamber 139 and the first discharge space 145 to communicate with each other, and a suction hole 151 that allows the first compression chamber 139 and the first suction space 141 to communicate with each other. ing. The discharge space 145 side of the discharge hole 149 is covered with a valve 153. The first compression chamber 139 side of the suction hole 151 is covered with a valve 155.

  The second cylinder body 126 of the second cylinder portion 122 has an inner flange 134 at the inner end, and has a substantially cylindrical shape coaxial with the shaft 109. The inner surface 128 of the second cylinder body 126 is fitted to the side surface 130 of the second piston 114 to support the second piston 114 so as to be slidable. Seal members 132, 132 are provided on the side surface 130 of the second piston 114.

A second lid member 136 is fixed to the outside of the second cylinder body 126. A second suction space 142 and a second discharge space 146 are formed on the inner surface of the second lid member 136. The second suction space 142 communicates with the secondary side pipe 33 of the secondary side cycle 7 through the second suction hole 144. The second discharge space 146 communicates with the secondary side pipe 33 of the secondary side cycle 7 through the second discharge hole 148.
A second valve member 138 is attached between the second cylinder body 126 and the second lid member, and the second lid member 136 and the second valve member 138 allow the outer opening of the second cylinder body 126 to be opened. Is sealed. A second compression chamber 140 surrounded by the second lid member 136, the second valve member 138, the inner surface 128 of the second cylinder body 126 and the reduced diameter portion 118 of the second piston 114 is formed.
The second valve member 138 is provided with a discharge hole 150 that connects the second compression chamber 140 and the second discharge space 146, and a suction hole 152 that connects the second compression chamber 140 and the second suction space 142. ing. The discharge space 146 side of the discharge hole 150 is covered with a valve 154. The second compression chamber 140 side of the suction hole 152 is covered with a valve 156.

The can (tubular member) 157 has a cylindrical shape and is disposed so as to cover the shaft 109 with a space therebetween. The can 157 is made of, for example, a nonmagnetic material such as stainless steel or invar.
Both ends of the can 157 are attached to the first support member 159 and the second support member 160. Since the support member 159 is fixed to the inner flange 133 of the first cylinder main body 125 and the support member 160 is fixed to the inner flange 134 of the second cylinder main body 126, the can 157 is connected to the first cylinder portion 121. It is supported by the second cylinder part 122. The first cylinder part 121, the second cylinder part 122, and the can 157 form a sealed space.

A linear motor 161 is adopted as the driving means 107. A first permanent magnet 163 is attached to one end side (first piston 113 side) of the large-diameter portion 115 of the shaft 109, and a second permanent magnet 165 is attached to the other end side (second piston 114 side). The first permanent magnet 163 and the second permanent magnet 165 constitute a driven part of the linear motor 161.
The first permanent magnet 163 and the second permanent magnet 165 are each formed of a rare earth and have a donut shape whose outer diameter is substantially equal to the inner diameter of the can 157.
The first permanent magnet 163 and the second permanent magnet 165 are attached to the shaft 109 so that the other end side surface 163a of the opposing first permanent magnet 163 and the one end side surface 165a of the second permanent magnet 165 have the same polarity (for example, As shown in FIG. 7, it is attached so as to have an S pole).

The drive unit 167 of the linear motor 161 is provided with a first coil 169, a second coil 171, and a third coil 173 at equal intervals on the outside of the can 157 as viewed from one end side.
The first coil 169, the second coil 171, and the third coil 173 are wound or controlled such that surfaces facing each other have the same polarity. For example, as shown in FIG. 7, the other end side surface 169b of the first coil 169 and the one end side surface 171a of the second coil 171 are N poles, and the other end side surface 171b of the second coil 171 and one end side surface of the third coil 173 are. 173a is configured to be the S pole. For example, when the current flow to the winding is reversed, the other end side surface 169b of the first coil 169 and the one end side surface 171a of the second coil 171 are set to the S pole, and the other end side surface 171b of the second coil 171 is One end side surface 173a of the three coil 173 becomes an N pole.

Operation | movement of the refrigerant | coolant conveyance pump 1 concerning this embodiment demonstrated above is demonstrated.
The refrigerant transfer pump 1 sucks a refrigerant made of, for example, carbon dioxide that is transferred through the secondary side pipe 33 of the secondary side cycle 7 with a pressure of about 10 MPa during heating and about 4 MPa during cooling. The pressure is increased by about 3 to 0.5 MPa and discharged.

In FIG. 7, the second piston 114 moves to the other end side (the right side in FIG. 7), and the refrigerant sucked into the second compression chamber 140 by the second piston 114 passes through the second discharge hole 148, The state discharged to the secondary side pipe 33 of the side cycle 7 is shown.
When the current of the driving unit 167 of the linear motor 161 is switched from the state shown in FIG. 7, the other end side surface 169 b of the first coil 169 and the one end side surface 171 a of the second coil 171 are set to the S pole, and the other end side surface of the second coil 171. 171b and one end side surface 173a of the third coil 173 form an N pole. In this case, the south pole of the other end side surface 169 b of the first coil 169 attracts the north pole of the one end side surface 163 a of the first permanent magnet 163, and the south pole of the one end side surface 171 a of the second coil 171 is the first permanent magnet 163. A force acts to move the shaft 109 to one end side, repelling the south pole of the other end side surface 163b. This also applies to the second permanent magnet 165, a force for moving the shaft 109 to one end side. With such a force, the shaft 109 starts to move to one end side.

  When the second piston 114 starts moving toward the one end side together with the shaft 109, the valve 154 of the second valve member 138 is closed, and the communication between the second compression chamber 140 and the second discharge space 146 is cut off. At the same time, the valve 156 of the second valve member 138 opens to allow the second compression chamber 140 and the second suction space 142 to communicate with each other, so that the second compression chamber 140 has a suction hole 144, a second suction space 142, and a second suction space. The refrigerant is sucked from the secondary side pipe 33 via the suction hole 152.

  On the other hand, since the first piston 113 is simultaneously moved to one end side, the valve 155 of the first valve member 137 is closed, and the communication between the first compression chamber 139 and the first suction space 141 is cut off. At the same time, the valve 153 of the first valve member 137 is opened, and the first compression chamber 139 and the first discharge space 145 are communicated. Accordingly, the refrigerant is continuously discharged from the first compression chamber 139 to the secondary side pipe 33 of the secondary side cycle 7 via the discharge hole 149, the first discharge space 145, and the first discharge hole 147. .

Then, when, for example, the current flowing direction of the driving unit 167 of the linear motor 161 is switched at the timing when the one end side surface 163a of the first permanent magnet 163 reaches the other end side surface 169b of the first coil 169, as shown in FIG. It becomes a polar relationship. As a result, the shaft 109 starts to move to the other end side due to the polarity relationship between the driving unit 167 and the driven unit, and the operation opposite to that described above is performed.
That is, the valve 153 of the first valve member 137 is closed, and the communication between the first compression chamber 139 and the first discharge space 145 is cut off. At the same time, the valve 155 of the first valve member 137 is opened to allow the first compression chamber 139 and the first suction space 141 to communicate with each other, so that the suction hole 143, the first suction space 141, and the first suction space 141 are connected to the first compression chamber 139. The refrigerant is sucked from the secondary side pipe 33 via the suction hole 151.

  On the other hand, since the second piston 114 moves to the other end side at the same time, the valve 156 of the second valve member 138 is closed, and the communication between the second compression chamber 140 and the second suction space 142 is cut off. At the same time, the valve 154 of the second valve member 138 is opened to allow the second compression chamber 140 and the second discharge space 146 to communicate with each other. Thereby, the refrigerant is continuously discharged from the second compression chamber 140 to the secondary side pipe 33 of the secondary side cycle 7 via the discharge hole 150, the second discharge space 146 and the second discharge hole 148. .

  As described above, when the first piston 113 discharges the refrigerant from the first compression chamber 139 to the secondary side pipe 33, the refrigerant sucked from the secondary side pipe 33 into the second compression chamber 140 is back to the first piston 113. When the second piston 114 discharges the refrigerant from the first compression chamber 140 to the secondary side pipe 33, the refrigerant sucked into the first compression chamber 139 from the secondary side pipe 33 is with respect to the second piston 114. Configure back pressure. Since the load applied to both ends of the piston member 103 is substantially balanced in this way, even when handling a high-pressure refrigerant in a supercritical state such as during heating, the piston member 103 is smoothly balanced with a driving force corresponding to the differential pressure. It can be moved and there is no fluctuation in driving force, and a balanced operation can be performed.

  In addition, since either one of the first compression chamber 139 and the second compression chamber 140 constantly sucks the refrigerant, when maintaining the same suction amount as compared with intermittent refrigerant suction, The suction speed of the refrigerant will decrease. As described above, when the refrigerant suction speed decreases, pressure loss caused by friction, flow path resistance, etc. can be reduced when the refrigerant is sucked. However, it is possible to prevent the situation where the liquid and gas are separated into two layers and cannot be compressed.

Further, by changing the polarities of the first coil 169, the second coil 171, and the third coil 173 that constitute the drive unit 167 of the linear motor 161, the above-described operation is repeated, and the refrigerant flows into the first discharge hole 153. Although it is alternately from the second discharge holes 154, it is continuously discharged to the secondary side pipe 33 of the secondary side cycle 7.
Therefore, since the discharge amount to the secondary side pipe 33 is always substantially constant, the refrigerant conveyed through the secondary side pipe 33 does not periodically increase and decrease. Thereby, since the refrigerant | coolant which flows through the indoor heat exchanger 31 does not pulsate, the heat exchange in an indoor side can be performed stably.

  Furthermore, the refrigerant conveyed in the supercritical state during the heating operation cannot convey the lubricating oil because the density is smaller than that of the lubricating oil. However, the linear motor 161 is used as a driving unit, and the first cylinder unit 121 and the second cylinder are used. Since there is no rotating portion in the refrigerant sealed space formed by the cylinder portion 122 and the can 157, stable operation can be performed for a long period of time even if sufficient lubrication is not possible.

  Since the first cylinder part 121, the second cylinder part 122, and the can 157 form a sealed space, for example, a high-pressure refrigerant during heating is between the first cylinder body 125 and the first piston 113 and Even if leaking from the seal between the second cylinder body 126 and the second piston 114, the refrigerant does not leak to the outside by the can 157. Therefore, it can operate for a long time without replenishing the refrigerant, and it is possible to prevent adverse effects on the surrounding environment.

3 and FIG. 4 are provided on the side surface 129 of the first piston 121 and the side surface 130 of the second piston 122, and the inner surface 127 of the first cylinder body 125 or the second cylinder body 126, respectively. The dynamic pressure of the refrigerant entering the gap with the inner surface 128 may be increased to prevent mutual contact.
Further, as shown in FIG. 11, one end side of the shaft 109 may be supported by a linear guide 211 and the other end side may be supported by a linear guide 212. In this case, since the shaft 109 is supported by the linear guides 211 and 212, it is not displaced in the radial direction. Therefore, the contact between the first piston 121 and the first cylinder body 125 and the second piston 122 and the second cylinder are eliminated. Contact with the main body 126 can be prevented.

    Moreover, the side surface 129 of the first piston 121 and the side surface 130 of the second piston 122 may be structured as shown in FIGS. 5 and 6 to enhance the sealing effect.

Hereinafter, the operation and effect of the refrigerant transfer pump according to the present embodiment will be described.
According to the refrigerant transport pump 1 according to the present embodiment, when the shaft 109 is driven to one side by the driving unit 107, the refrigerant is discharged from the first compression chamber 139 on one side via the first discharge hole 147. At the same time, the refrigerant is sucked into the second compression chamber 140 on the other side. Then, when the shaft 109 is driven in the opposite direction by the driving means 107, contrary to the above, the refrigerant is discharged from the second compression chamber 140 on the other side and simultaneously sucked into the first compression chamber 139. By repeating this, the refrigerant is continuously sucked into the refrigerant transfer pump 1 and continuously discharged.
As described above, when the suction and discharge of the refrigerant are continuously performed, a large load at the time of constant discharge and a small load at the time of suction are applied, so that fluctuations in driving force can be reduced. In addition, the refrigerant is always supplied to the secondary side pipe 33 of the secondary side cycle 7 in a state where the required amount is continuously, that is, in a state where the difference between the part with a large supply amount and the part with a small supply amount is small (pulsation is small) Heat exchange in the secondary cycle 7 can be performed stably.
Further, for example, if the area of the piston and the stroke are the same, the suction volume of the compression chamber is twice that of a single pump. If the suction amount of the refrigerant is the same, the suction speed of the refrigerant, that is, the suction amount per unit time is half that of a pump with one compression chamber. Thus, when the suction speed of the refrigerant is reduced, pressure loss caused by factors such as friction and flow path resistance when the refrigerant is sucked can be reduced. Therefore, since the pressure loss when the refrigerant is sucked can be reduced, for example, in the cooling operation in which heat is transferred as latent heat at the time of phase change, the pressure in the compression chamber decreases and the liquid and gas are separated into two layers. It is possible to prevent a situation in which compression is not possible.

Further, according to the refrigerant transport pump 1 of the present embodiment, the linear motor 161 is adopted as the driving means, and the driving unit 167 of the linear motor 161 is provided outside the can 157. A rotating part can be eliminated in the space formed by the cylinder part 122 and the can 157. For this reason, the refrigerant transfer pump 1 does not require sufficient lubrication. Therefore, even if there is a state in which the lubricating oil cannot be transferred due to a density difference, such as a refrigerant transferred in a supercritical state during heating operation, the refrigerant transfer pump 1 Does not affect functionality. Therefore, the refrigerant conveyance pump can perform stable operation over a long period of time.
In addition, since the can 157 is attached to the first cylinder part 121 and the second cylinder part 122 so as to cover the shaft 109, a sealed space is formed by the first cylinder part 121, the second cylinder part 122, and the can 157. It is formed. For this reason, since the refrigerant leaking from the seal between the first cylinder part 121 and the first piston 113 and between the second cylinder part 122 and the second piston 114 is prevented from leaking outside by the can 157, It can be operated for a long time without replenishing the refrigerant, and it can prevent adverse effects on the surrounding environment.

[Third embodiment]
Next, the refrigerant transfer pump 1 according to the third embodiment of the present invention will be described with reference to FIGS.
Since the air conditioner 3 using the refrigerant transport pump 1 according to the present embodiment is the same as that described in the first embodiment, the description thereof is omitted.
Further, the refrigerant transport pump 1 in the present embodiment is different from that in the second embodiment described above in that the configuration of the drive means 107 and the can 157 are provided with a sleeve as a reinforcing member. Since other components are the same as those of the second embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 2nd Embodiment mentioned above.

A linear motor 181 is adopted as the driving means 107. The linear motor 181 is provided with a drive unit 183 and a driven unit 185.
The driven portion 185 is attached to the first inner permanent magnet group 187 attached to one end side (first piston 113 side) of the large diameter portion 115 of the shaft 109 and to the other end side (second piston 114 side). The second inner permanent magnet group 188 is provided.
As shown in FIG. 9, the second inner permanent magnet group 188 includes four permanent magnets 190 attached around the large diameter portion 115 at equal intervals. One permanent magnet 190 has different polarities in the radial direction (one end is N-pole and the other end is S-pole), and the polarities of the outer ends of adjacent permanent magnets 190 are different from each other (a certain one If the outer end is an N pole, the two adjacent outer ends are S poles).

  The first inner permanent magnet group 187 is also composed of four permanent magnets 189 arranged in the same manner as the second inner permanent magnet group 188. The permanent magnet 189 of the first inner permanent magnet group 187 and the permanent magnet 190 of the second inner permanent magnet group 188 are attached at the same phase in the circumferential direction, that is, at positions overlapping in the axial direction. And the permanent magnet 189 of the 1st inner permanent magnet group 187 and the permanent magnet 190 of the 2nd inner permanent magnet group 188 in the position which overlaps with an axial direction are comprised so that the polarity of an outer end part may mutually differ. .

The drive unit 183 of the linear motor 181 includes a general-purpose motor 191 that serves as a drive source, a crank 193 that is attached to the rotary shaft 192 of the general-purpose motor 191 and converts the rotary motion into a reciprocating motion, and an action unit 195 that is attached to the crank 193. And are provided.
The action portion 195 includes a cylindrical outer coupling 196 having the same axial center as the shaft 109, a first outer permanent magnet group 197 attached to one end side (first piston 113 side) of the outer coupling 196, and A second outer permanent magnet group 198 attached to the other end side (second piston 114 side) of the outer coupling 196 is provided.

  As shown in FIG. 9, the second outer permanent magnet group 198 includes four permanent magnets 200 attached to the inner peripheral side of the outer coupling 196 at equal intervals. One permanent magnet 200 has different polarities in the radial direction (one end is N pole and the other end is S pole), and the polarities of the inner ends of adjacent permanent magnets 200 are different from each other (a certain one If the inner end is N pole, the two adjacent outer ends are S poles).

  The first outer permanent magnet group 197 is also composed of four permanent magnets 199 arranged in the same manner as the second outer permanent magnet group 198. The permanent magnet 199 of the first outer permanent magnet group 197 and the permanent magnet 200 of the second outer permanent magnet group 198 are attached at the same phase in the circumferential direction, that is, at positions overlapping in the axial direction. And the permanent magnet 189 of the 1st outer permanent magnet group 197 and the permanent magnet 200 of the 2nd outer permanent magnet group 198 in the position which overlaps with an axial direction are comprised so that the polarities of an inner end may mutually differ.

The outer coupling 196 is arranged so that the permanent magnets 190 of the second inner permanent magnet group 188 and the permanent magnets 200 of the first outer permanent magnet group 198 are opposed to each other with the can 157 interposed therebetween. Further, the opposing end portions of the permanent magnet 190 and the permanent magnet 200 have different polarities (one is an N pole and the other is an S pole) and are attracted to each other. A set of the permanent magnet 190 and the permanent magnet 200 having such a relationship is referred to as a magnet coupling.
Similarly, the permanent magnets 189 of the first inner permanent magnet group 187 and the permanent magnets 199 of the first outer permanent magnet group 197 are arranged so that different polarities face each other across the can 157 and attract each other. Yes.

As described above, the shaft 109 is pulled in the radial direction by the outer coupling 196 at four positions arranged at equal intervals in the circumferential direction, so that the mutual pulling force is canceled and the center position can be maintained. Become.
In this embodiment, the number of the four positions is set in consideration of the balance of the magnetic force flow 205. However, if the number of the positions is three or more, the function of maintaining the shaft 109 at the center position is achieved.

A thick cylindrical sleeve 201 is provided on the outer peripheral side of the can 157. The sleeve 201 is attached to the first flange 159 and the second flange 160 so that the inner periphery thereof is in contact with the can 157.
The sleeve 201 has a function of reinforcing the strength of the can 157. For this reason, the can 157 does not require high strength in spite of being subjected to a high pressure such as a supercritical state.
On the circumferential surface of the sleeve, holes 203 extending in the axial direction are punched at four locations at equal intervals in the circumferential direction. The first outer permanent magnet group 197 and the second outer permanent magnet group 198 attached to the outer coupling 196 are inserted into the hole 203 and are disposed in proximity to the can 157. The axial length of the hole 203 is larger than the distance that the outer coupling 196 moves in the axial direction.

  The crank 193 performs a function of connecting the rotating shaft 192 of the general-purpose motor 191 and the outer coupling 196, converting the rotation of the rotating shaft 192, and reciprocating the outer coupling 196 in the axial direction. .

Operation | movement of the refrigerant | coolant conveyance pump 1 concerning this embodiment demonstrated above is demonstrated.
The refrigerant transfer pump 1 sucks a refrigerant made of, for example, carbon dioxide that is transferred through the secondary side pipe 33 of the secondary side cycle 7 with a pressure of about 10 MPa during heating and about 4 MPa during cooling. The pressure is increased by about 3 to 0.5 MPa and discharged.

The first outer permanent magnet group 197 and the second outer permanent magnet group 198 attached to the outer coupling 196 form a magnet coupling with the first inner permanent magnet group 187 and the second inner permanent magnet group 188, respectively. Therefore, the heel also functions as an integral object due to the magnetic force.
Therefore, as the outer coupling 196 moves in the axial direction, the shaft 109 to which the first inner permanent magnet group 187 and the second inner permanent magnet group 188 are fixed moves integrally.
Moreover, since the thickness of the can 157 is reduced, the first outer permanent magnet group 197 and the second outer permanent magnet group 198 are respectively formed by a first inner permanent magnet group 187 and a second inner permanent magnet group 188, respectively. The magnetic force attracting the two is increased due to the close arrangement. For this reason, the function as an integral object can be enhanced, or the apparatus can be miniaturized with the same ability.

In FIG. 8, the second piston 114 moves to the other end side (the right side in FIG. 8), and the refrigerant sucked into the second compression chamber 140 by the second piston 114 passes through the second discharge hole 148 and enters the secondary side. The state discharged to the secondary side pipe 33 of the side cycle 7 is shown.
From this state, the operation of the refrigerant transfer pump 1 will be described. The general-purpose motor 191 is activated and the rotating shaft 192 rotates. Along with this, the crank 193 converts the rotary motion of the rotary shaft 192 into a linear motion and moves the outer coupling 196 to one end side.

  The first outer permanent magnet group 197 and the second outer permanent magnet group 198 attached to the outer coupling 196 are the same as the first inner permanent magnet group 187 and the second inner permanent magnet group 188, respectively. Therefore, the shaft 109 to which the first inner permanent magnet group 187 and the second inner permanent magnet group 188 are fixed moves to one end side as the outer coupling 196 moves to one end side. When the shaft 109 moves, the second piston 114 fixed to the shaft 109 moves.

  When the second piston 114 starts to move toward one end, the valve 154 of the second valve member 138 is closed, and the communication between the second compression chamber 140 and the second discharge space 146 is cut off. At the same time, the valve 156 of the second valve member 138 opens to allow the second compression chamber 140 and the second suction space 142 to communicate with each other, so that the second compression chamber 140 has a suction hole 144, a second suction space 142, and a second suction space. The refrigerant is sucked from the secondary side pipe 33 via the suction hole 152.

)
On the other hand, since the first piston 113 is simultaneously moved to one end side, the valve 155 of the first valve member 137 is closed, and the communication between the first compression chamber 139 and the first suction space 141 is cut off. At the same time, the valve 153 of the first valve member 137 is opened, and the first compression chamber 139 and the first discharge space 145 are communicated. Accordingly, the refrigerant is continuously discharged from the first compression chamber 139 to the secondary side pipe 33 of the secondary side cycle 7 via the discharge hole 149, the first discharge space 145, and the first discharge hole 147. .

  When the rotation shaft 192 rotates halfway, the outer coupling 196 approaches the one end side most, and when the rotation shaft 192 further rotates, the outer coupling 196 starts to move from one end side to the other end side. Along with this, the shaft 109 starts to move to the other end side.

  When the shaft 109 moves to the other end side, the valve 153 of the first valve member 137 is closed, and the communication between the first compression chamber 139 and the first discharge space 145 is cut off. At the same time, the valve 155 of the first valve member 137 is opened to allow the first compression chamber 139 and the first suction space 141 to communicate with each other, so that the suction hole 143, the first suction space 141, and the first suction space 141 are connected to the first compression chamber 139. The refrigerant is sucked from the secondary side pipe 33 via the suction hole 151.

  On the other hand, since the second piston 114 moves to the other end side at the same time, the valve 156 of the second valve member 138 is closed, and the communication between the second compression chamber 140 and the second suction space 142 is cut off. At the same time, the valve 154 of the second valve member 138 is opened to allow the second compression chamber 140 and the second discharge space 146 to communicate with each other. Thereby, the refrigerant is continuously discharged from the second compression chamber 140 to the secondary side pipe 33 of the secondary side cycle 7 via the discharge hole 150, the second discharge space 146 and the second discharge hole 148. .

  As described above, when the first piston 113 discharges the refrigerant from the first compression chamber 139 to the secondary side pipe 33, the refrigerant sucked from the secondary side pipe 33 into the second compression chamber 140 is back to the first piston 113. When the second piston 114 discharges the refrigerant from the first compression chamber 140 to the secondary side pipe 33, the refrigerant sucked into the first compression chamber 139 from the secondary side pipe 33 is with respect to the second piston 114. Configure back pressure. Since the load applied to both ends of the piston member 103 is substantially balanced in this way, even when handling a high-pressure refrigerant in a supercritical state such as during heating, the piston member 103 is smoothly balanced with a driving force corresponding to the differential pressure. It can be moved and there is no fluctuation in driving force, and a balanced operation can be performed.

  In addition, since either one of the first compression chamber 139 and the second compression chamber 140 constantly sucks the refrigerant, when maintaining the same suction amount as compared with intermittent refrigerant suction, The suction speed of the refrigerant will decrease. As described above, when the refrigerant suction speed decreases, pressure loss caused by friction, flow path resistance, etc. can be reduced when the refrigerant is sucked. However, it is possible to prevent the situation where the liquid and gas are separated into two layers and cannot be compressed.

Further, by rotating the rotating shaft 192 by the general-purpose motor 191, the above-described operation is repeated, and the refrigerant is alternately continuously from the first discharge hole 153 and the second discharge hole 154, but continuously on the secondary side. It is discharged to the secondary side pipe 33 of the cycle 7.
Therefore, since the discharge amount to the secondary side pipe 33 is always substantially constant, the refrigerant conveyed through the secondary side pipe 33 does not periodically increase and decrease. Thereby, since the refrigerant | coolant which flows through the indoor heat exchanger 31 does not pulsate, the heat exchange in an indoor side can be performed stably.

  Further, since the members constituting the driving unit 183 of the linear motor 181 are general-purpose members such as the general-purpose motor 191, the crank 193, and the permanent magnets 189, 190, 199, and 200, and are inexpensive, the entire apparatus can be manufactured at low cost. . In addition, maintenance is easy because it is easily accessible from the outside. Furthermore, since the permanent magnets 189, 190, 199, and 200 are used, the generation of eddy current is reduced, so that the restriction on the materials used for members around the linear motor 181 can be relaxed.

  Furthermore, the refrigerant conveyed in the supercritical state during the heating operation cannot convey the lubricating oil because the density is smaller than that of the lubricating oil. However, the linear motor 181 is employed as the driving means, and the first cylinder unit 121 and the second cylinder Since there is no rotating portion in the refrigerant sealed space formed by the cylinder portion 122 and the can 157, stable operation can be performed for a long period of time even if sufficient lubrication is not possible.

  Since the first cylinder part 121, the second cylinder part 122, and the can 157 form a sealed space, for example, a high-pressure refrigerant during heating is between the first cylinder body 125 and the first piston 113 and Even if leaking from the seal between the second cylinder body 126 and the second piston 114, the refrigerant does not leak to the outside by the can 157. Therefore, it can operate for a long time without replenishing the refrigerant, and it is possible to prevent adverse effects on the surrounding environment.

3 and FIG. 4 are provided on the side surface 129 of the first piston 121 and the side surface 130 of the second piston 122, and the inner surface 127 of the first cylinder body 125 or the second cylinder body 126, respectively. The dynamic pressure of the refrigerant entering the gap with the inner surface 128 may be increased to prevent mutual contact.
Moreover, the side surface 129 of the first piston 121 and the side surface 130 of the second piston 122 may be structured as shown in FIGS. 5 and 6 to enhance the sealing effect.

Hereinafter, the operation and effect of the refrigerant transfer pump according to the present embodiment will be described.
In addition to the functions and effects that can be obtained in the second embodiment described above, the following functions and effects can be obtained.
That is, since the sleeve 201 is attached to the first cylinder portion 121 and the second cylinder portion 122 so as to cover the can 157 from the outside, the sleeve 201 reinforces the strength of the can 157. For this reason, the can 157 does not require a high strength in spite of being subjected to a high pressure such as a supercritical pressure, so that the thickness can be reduced.
Therefore, the distance between the action part 196 constituting the drive part 183 of the linear motor 181 disposed in the hole 203 provided in the sleeve 201 and the driven part 185 of the linear motor 181 attached to the shaft 109 is shortened. Therefore, the magnetic force which the action part 196 gives to the driven part 185 increases. For this reason, the driving force of the linear motor 181 can be increased and the size can be reduced.

Further, the drive unit 183 of the linear motor 181 is mainly composed of a general-purpose motor 191, a crank 193 that converts rotation into reciprocating motion, and permanent magnets 189, 190, 199, and 200, so that each component is inexpensive. Therefore, it can be manufactured inexpensively as a whole, and maintenance can be easily performed.
In addition, since permanent magnets 189, 190, 199, and 200 are employed as the action portion 196, the generation of eddy current accompanying magnetic field fluctuations is reduced. For this reason, restrictions on the materials used for the peripheral members are relaxed, and the degree of freedom in design can be increased.

[Fourth embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG.
Since the air conditioner 3 using the refrigerant transport pump 1 according to the present embodiment is the same as that described in the first embodiment, the description thereof is omitted.
Further, the refrigerant transport pump 1 in the present embodiment is different from that of the second embodiment described above in the structure of the shaft 109 of the piston member 103 and the configuration of the driving means 107. Since other components are the same as those of the second embodiment described above, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 2nd Embodiment mentioned above.

The piston member 103 includes a shaft 109, a first piston 113 fixed to one end portion 111 of the shaft 109, and a second piston 114 fixed to the other end portion 112 of the shaft 109.
The shaft 109 is composed of four rod-shaped members 221. The four rod-shaped members 221 are arranged at equal intervals on a circumference having the same axis as the axis of the first piston 113.
Both ends of the rod-shaped member 221 are fixed to the first piston 113 and the second piston 114, respectively, and a large-diameter portion 223 is provided at the center in the longitudinal direction.

The can (tubular member) 225 has a cylindrical shape and is disposed so as to cover each bar-shaped member 221 with a space therebetween. The can 225 is made of a nonmagnetic material such as stainless steel or invar.
The first support member 159 is provided with a hole 227 for attaching the can 225. The second support member 160 is also provided with a hole 228 at a position facing the hole 227. Both ends of the can 225 are attached to the hole 227 of the first support member 159 and the hole 228 of the second support member 160. Since the support member 159 is fixed to the inner flange 133 of the first cylinder main body 125 and the support member 160 is fixed to the inner flange 134 of the second cylinder main body 126, the can 157 is connected to the first cylinder portion 121. It is supported by the second cylinder part 122. The first cylinder part 121, the second cylinder part 122, and the can 157 form a sealed space.

A linear motor 231 is adopted as the driving means 107. A first permanent magnet 233 is attached to one end side (first piston 113 side) of the large diameter portion 223 of each rod-shaped member 221, and a second permanent magnet 235 is attached to the other end side (second piston 114 side). Four sets of the first permanent magnet 233 and the second permanent magnet 235 constitute the driven portion of the linear motor 231.
The first permanent magnet 233 and the second permanent magnet 235 are each formed of a rare earth and have a donut shape whose outer diameter is substantially equal to the inner diameter of the can 225.
The first permanent magnet 163 and the second permanent magnet 165 are attached to the rod-shaped member 221, and the other end side surface 233a of the opposing first permanent magnet 233 and the one end side surface 235a of the second permanent magnet 235 have the same polarity ( For example, as shown in FIG. 12, it is configured to have an S pole).

The drive unit 237 of the linear motor 231 is provided with a first coil 239, a second coil 241, and a third coil 243 as viewed from one end side at equal intervals outside each can 225.
The first coil 239, the second coil 241, and the third coil 243 are wound or controlled such that surfaces facing each other have the same polarity. For example, as shown in FIG. 12, the other end side surface 239b of the first coil 239 and the one end side surface 241a of the second coil 241 are N poles, and the other end side surface 241b of the second coil 241 and one end side surface of the third coil 243 243a is configured as the S pole. For example, when the current flow to the winding is reversed, the other end side surface 239b of the first coil 239 and the one end side surface 241a of the second coil 241 are set to the S pole, and the other end side surface 241b of the second coil 241 is One end side surface 243a of the three coil 243 becomes an N pole.

Operation | movement of the refrigerant | coolant conveyance pump 1 concerning this embodiment demonstrated above is demonstrated.
The refrigerant transfer pump 1 sucks a refrigerant made of, for example, carbon dioxide that is transferred through the secondary side pipe 33 of the secondary side cycle 7 with a pressure of about 10 MPa during heating and about 4 MPa during cooling. The pressure is increased by about 3 to 0.5 MPa and discharged.

In FIG. 12, the second piston 114 moves to the other end side (the right side in FIG. 12), and the refrigerant sucked into the second compression chamber 140 by the second piston 114 passes through the second discharge hole 148 and enters the secondary side. The state discharged to the secondary side pipe 33 of the side cycle 7 is shown.
When the current of the drive unit 237 of the linear motor 231 is switched from the state shown in FIG. The other end side surface 241b and the one end side surface 243a of each third coil 243 form an N pole. In this case, the south pole of the other end side surface 239b of each first coil 239 attracts the north pole of the one end side surface 233a of each first permanent magnet 233, and the south pole of the one end side surface 241a of each second coil 241 becomes each first pole. A force acts to move each rod-shaped member 221 toward one end side, repelling the south pole of the other end side surface 233b of the permanent magnet 233. This also applies to each second permanent magnet 235 a force for moving each rod-shaped member 221 to one end side. By such a force, the shaft 109 constituted by the rod-shaped member 221 starts to move toward one end side.

  When the second piston 114 starts moving toward the one end side together with the shaft 109, the valve 154 of the second valve member 138 is closed, and the communication between the second compression chamber 140 and the second discharge space 146 is cut off. At the same time, the valve 156 of the second valve member 138 opens to allow the second compression chamber 140 and the second suction space 142 to communicate with each other, so that the second compression chamber 140 has a suction hole 144, a second suction space 142, and a second suction space. The refrigerant is sucked from the secondary side pipe 33 via the suction hole 152.

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On the other hand, since the first piston 113 is simultaneously moved to one end side, the valve 155 of the first valve member 137 is closed, and the communication between the first compression chamber 139 and the first suction space 141 is cut off. At the same time, the valve 153 of the first valve member 137 is opened, and the first compression chamber 139 and the first discharge space 145 are communicated. Accordingly, the refrigerant is continuously discharged from the first compression chamber 139 to the secondary side pipe 33 of the secondary side cycle 7 via the discharge hole 149, the first discharge space 145, and the first discharge hole 147. .

Then, when, for example, the current flowing direction of the drive unit 237 of the linear motor 231 is switched at the timing when the one end side surface 233a of each first permanent magnet 233 reaches the other end side surface 239b of each first coil 239, FIG. The polarity relationship is as shown. In this way, the shaft 109 starts to move to the other end side due to the polarity relationship between the drive unit 237 and the driven unit, and the reverse operation is performed.
That is, the valve 153 of the first valve member 137 is closed, and the communication between the first compression chamber 139 and the first discharge space 145 is cut off. At the same time, the valve 155 of the first valve member 137 is opened to allow the first compression chamber 139 and the first suction space 141 to communicate with each other, so that the suction hole 143, the first suction space 141, and the first suction space 141 are connected to the first compression chamber 139. The refrigerant is sucked from the secondary side pipe 33 via the suction hole 151.

  On the other hand, since the second piston 114 moves to the other end side at the same time, the valve 156 of the second valve member 138 is closed, and the communication between the second compression chamber 140 and the second suction space 142 is cut off. At the same time, the valve 154 of the second valve member 138 is opened to allow the second compression chamber 140 and the second discharge space 146 to communicate with each other. Thereby, the refrigerant is continuously discharged from the second compression chamber 140 to the secondary side pipe 33 of the secondary side cycle 7 via the discharge hole 150, the second discharge space 146 and the second discharge hole 148. .

  As described above, when the first piston 113 discharges the refrigerant from the first compression chamber 139 to the secondary side pipe 33, the refrigerant sucked from the secondary side pipe 33 into the second compression chamber 140 is back to the first piston 113. When the second piston 114 discharges the refrigerant from the first compression chamber 140 to the secondary side pipe 33, the refrigerant sucked into the first compression chamber 139 from the secondary side pipe 33 is with respect to the second piston 114. Configure back pressure. Since the load applied to both ends of the piston member 103 is substantially balanced in this way, even when handling a high-pressure refrigerant in a supercritical state such as during heating, the piston member 103 is smoothly balanced with a driving force corresponding to the differential pressure. It can be moved and there is no fluctuation in driving force, and a balanced operation can be performed.

  In addition, since either one of the first compression chamber 139 and the second compression chamber 140 constantly sucks the refrigerant, when maintaining the same suction amount as compared with intermittent refrigerant suction, The suction speed of the refrigerant will decrease. As described above, when the refrigerant suction speed decreases, pressure loss caused by friction, flow path resistance, etc. can be reduced when the refrigerant is sucked. However, it is possible to prevent the situation where the liquid and gas are separated into two layers and cannot be compressed.

Further, by changing the polarities of the first coils 239, the second coils 241, and the third coils 243 constituting the driving unit 237 of the linear motor 231, the above-described operation is repeated, and the refrigerant is discharged into the first discharge. Although it is alternately from the hole 153 and the second discharge hole 154, it is continuously discharged to the secondary side pipe 33 of the secondary side cycle 7.
Therefore, since the discharge amount to the secondary side pipe 33 is always substantially constant, the refrigerant conveyed through the secondary side pipe 33 does not periodically increase and decrease. Thereby, since the refrigerant | coolant which flows through the indoor heat exchanger 31 does not pulsate, the heat exchange in an indoor side can be performed stably.

  Further, the refrigerant conveyed in the supercritical state during the heating operation cannot convey the lubricating oil because the density is smaller than that of the lubricating oil. However, the linear motor 231 is adopted as the driving unit, and the first cylinder unit 121 and the second Since there is no rotating part in the refrigerant sealed space formed by the cylinder part 122 and each can 225, stable operation can be performed for a long period of time without sufficient lubrication.

  Further, since the shaft is composed of four rod-shaped members 221, the cross-sectional area of each rod-shaped member 221 is small if the diameter of the piston member 103 is the same. When the cross-sectional area of the rod-shaped member 221 is reduced, the diameter of the can 225 that covers the rod-like member 221 can be reduced, so that the pressure resistance of the can 225 is improved. If the same pressure is applied, the thickness of the can 225 can be reduced as compared with the shaft 109 having a single structure. Therefore, since the drive part 237 of the linear motor 221 provided outside the can 225 can be disposed close to the can 225, the driving force of the linear motor 221 can be increased.

  Furthermore, since four rod-shaped members 221 are arranged at equal intervals on the same circumference, the rod-shaped members 221 have a point-symmetric positional relationship. Therefore, the driving force balance is good.

  Since the first cylinder 121, the second cylinder 122, and the can 225 form a sealed space, for example, a high-pressure refrigerant during heating is between the first cylinder main body 125 and the first piston 113 and Even if leaking from the seal between the second cylinder body 126 and the second piston 114, the refrigerant does not leak to the outside by the can 157. Therefore, it can operate for a long time without replenishing the refrigerant, and it is possible to prevent adverse effects on the surrounding environment.

  3 and FIG. 4 are provided on the side surface 129 of the first piston 121 and the side surface 130 of the second piston 122, and the inner surface 127 of the first cylinder body 125 or the second cylinder body 126, respectively. The dynamic pressure of the refrigerant entering the gap with the inner surface 128 may be increased to prevent mutual contact.

  Moreover, the side surface 129 of the first piston 121 and the side surface 130 of the second piston 122 may be structured as shown in FIGS. 5 and 6 to enhance the sealing effect.

Hereinafter, the operation and effect of the refrigerant transfer pump according to the present embodiment will be described.
In addition to the refrigerant transfer pump 1 according to the present embodiment described in the second embodiment, the shaft 109 includes four rod-shaped members that connect the first piston 113 and the second piston 114, respectively. Since it is comprised by 221, the cross-sectional area of each rod-shaped member 221 becomes small. When the cross-sectional area of the rod-shaped member 221 is reduced, the cross-sectional area of the can 225 that covers the bar-shaped member 221 can be reduced, so that the pressure resistance strength of the can 225 can be improved and the can 225 can be configured to be thin. Accordingly, the driving unit 237 of the linear motor 231 provided outside the can 225 can be disposed close to the non-driving unit provided inside the can 225, so that the driving force of the linear motor 231 is increased. Can do.
In addition, it is possible to optimally arrange a comprehensive magnetic circuit, and to improve driving efficiency.

  In addition, in this embodiment, although the rod-shaped member 221 was comprised with four pieces, it is not limited to this, What is necessary is just two or more. Note that three or more are desirable from the viewpoint of driving balance, and for example, it is more desirable to have a point-symmetrical positional relationship such as four.

It is a schematic block diagram of the air conditioner using the refrigerant | coolant conveyance pump of this invention. It is sectional drawing which shows the refrigerant | coolant conveyance pump concerning 1st embodiment of this invention. It is sectional drawing which shows a part of refrigerant transport pump concerning 1st embodiment of this invention. It is sectional drawing similar to FIG. 3 which shows other embodiment of this invention. It is sectional drawing similar to FIG. 3 which shows other embodiment of this invention. It is sectional drawing similar to FIG. 3 which shows other embodiment of this invention. It is sectional drawing which shows the refrigerant | coolant conveyance pump concerning 2nd embodiment of this invention. It is sectional drawing which shows the refrigerant | coolant conveyance pump concerning 3rd embodiment of this invention. It is XX sectional drawing of FIG. FIG. 10 is a perspective view showing the sleeve of FIG. 9. It is sectional drawing which shows the refrigerant | coolant conveyance pump concerning other embodiment of this invention. It is sectional drawing which shows the refrigerant | coolant conveyance pump concerning 4th embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigerant conveyance pump 45 Drive means 47 Shaft 49 1st piston 50 2nd piston 63 1st cylinder part 64 2nd cylinder part 75 1st discharge hole 76 2nd discharge hole 81 1st compression chamber 82 2nd compression chamber 85 Side face 86 Side surface 92 Can 93 Suction hole 103 Projection part 107 Drive means 109 Shaft 113 First piston 114 Second piston 121 First cylinder part 122 Second cylinder part 139 First compression chamber 140 Second compression chamber 143 First suction hole 144 Second Suction hole 147 First discharge hole 148 Second discharge hole 157 Can 161 Linear motor 167 Drive part 181 Linear motor 183 Drive part 191 General-purpose motor 193 Crank 196 Action part 201 Sleeve 203 Hole part 225 Can 231 Linear motor 237 Drive part

Claims (8)

In the refrigerant transport pump used in the secondary cycle, which is transported as sensible heat in a supercritical state during heating, and is transported as latent heat during phase change during cooling,
A shaft that has pistons at both ends and is provided so as to be able to reciprocate in the direction of the piston connection axis,
A cylinder portion that slidably supports each piston from the outside;
A compression chamber formed between the piston and the cylinder portion and communicated with the suction portion and the discharge portion;
And a drive means for reciprocally driving the shaft in the axial direction. A tubular member is attached to the cylinder so as to cover the shaft,
Adopting a linear motor as the driving means,
The refrigerant conveyance pump according to claim 1, wherein a drive unit for the linear motor is provided outside the tubular member. The refrigerant transport pump according to claim 2, wherein the tubular member is made of a non-magnetic material. The shaft is composed of a plurality of rod-shaped members that connect the pistons at both ends,
The refrigerant transport pump according to claim 2 or 3, wherein the tubular member is provided so as to cover the rod-shaped members. A sleeve is attached to the cylinder part so as to cover the tubular member from the outside,
The sleeve is provided with a hole formed so as to penetrate in the thickness direction,
The refrigerant conveying pump according to any one of claims 2 to 4, wherein an action portion constituting a driving portion of the linear motor is disposed in the hole portion. The refrigerant transfer pump according to claim 5, wherein the sleeve is made of a non-magnetic material. The drive unit of the linear motor is
A general-purpose motor;
A crank connected to the rotary shaft of the general-purpose motor and converting the rotation of the rotary shaft into a reciprocating motion;
A refrigerant transfer pump according to any one of claims 2 to 6, further comprising a permanent magnet attached to a tip of the crank. 8. The projection according to claim 1, wherein a protrusion is provided at an intermediate position in a sliding direction on a side surface of the piston so that a gap with the cylinder portion is narrower than positions at both ends in the sliding direction. The refrigerant transport pump described in the above.

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