U.S. patent application number 12/873599 was filed with the patent office on 2011-03-10 for linear electric compressor and refrigerant circuit.
This patent application is currently assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. Invention is credited to Nobuaki Hoshino, Masahiro Kawaguchi, Yoshio Kimoto, Toru Onishi, Masaki Ota.
Application Number | 20110056235 12/873599 |
Document ID | / |
Family ID | 43477784 |
Filed Date | 2011-03-10 |
United States Patent
Application |
20110056235 |
Kind Code |
A1 |
Hoshino; Nobuaki ; et
al. |
March 10, 2011 |
LINEAR ELECTRIC COMPRESSOR AND REFRIGERANT CIRCUIT
Abstract
A refrigerant circuit includes a linear electric compressor
including a housing with a cylinder bore, a pair of end plates, a
valve unit, a piston, an urging device for urging the piston, a
coil generating electromagnetic force and a permanent magnet. The
permanent magnet cooperates with the urging device and the coil to
reciprocate the piston in the cylinder bore. The piston further
includes a piston rod and the urging device is provided around the
piston rod and a pair of piston heads integrally formed at opposite
ends of the piston rod. The diameter of the piston rod is smaller
than that of the piston head. The permanent magnet is provided on
the piston head and the coil surrounds the piston head. The housing
further includes a seat located between the pair of piston heads
and the urging device is provided between the seat and each of the
piston head.
Inventors: |
Hoshino; Nobuaki;
(Aichi-ken, JP) ; Kawaguchi; Masahiro; (Aichi-ken,
JP) ; Ota; Masaki; (Aichi-ken, JP) ; Kimoto;
Yoshio; (Aichi-ken, JP) ; Onishi; Toru;
(Aichi-ken, JP) |
Assignee: |
KABUSHIKI KAISHA TOYOTA
JIDOSHOKKI
Kariya-shi
JP
|
Family ID: |
43477784 |
Appl. No.: |
12/873599 |
Filed: |
September 1, 2010 |
Current U.S.
Class: |
62/498 ;
417/416 |
Current CPC
Class: |
F04B 35/045 20130101;
F04B 39/12 20130101; F04B 49/065 20130101; F04B 2203/0204 20130101;
F04B 2203/0203 20130101 |
Class at
Publication: |
62/498 ;
417/416 |
International
Class: |
F25B 1/00 20060101
F25B001/00; F04B 35/04 20060101 F04B035/04 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 4, 2009 |
JP |
P2009-204288 |
Dec 14, 2009 |
JP |
P2009-283350 |
Claims
1. A linear electric compressor comprising: a housing having formed
therein a cylinder bore; a pair of end plates joined to opposite
ends of the housing; a valve unit provided between the cylinder
bore and the end plate, wherein a compression chamber is located on
the cylinder bore side of the valve unit and a discharge chamber or
a suction chamber is located on the end plate side of the valve
unit; a piston reciprocally-slidably received in the cylinder bore,
wherein the piston and the valve unit cooperate to form the
compression chamber in the cylinder bore; an urging device for
urging the piston in the direction for the piston to reciprocate; a
coil provided in the housing and generating electromagnetic force;
and a permanent magnet provided in the piston, the permanent magnet
cooperate with the urging device and the coil to reciprocate the
piston in the cylinder bore, wherein the piston includes: a piston
rod; and a pair of piston heads integrally formed at opposite ends
of the piston rod, the piston heads are slidable in the cylinder
bore, wherein the diameter of the piston rod is smaller than that
of the piston head, wherein the permanent magnet is provided on the
piston head and the coil surrounds the piston head; wherein the
housing includes: a seat located between the pair of piston heads,
wherein the urging device is provided around the piston rod between
the seat and each of the piston head.
2. The linear electric compressor according to claim 1, wherein the
housing includes: a cylinder block having formed therein the
cylinder bore; and a shell housing the cylinder block, wherein the
coil is provided between the shell and the cylinder block.
3. The linear electric compressor according to claim 2, wherein the
piston has a suction passage provided between the pair of piston
heads, the linear electric compressor further comprising: an
intermediate chamber provided in any one of the cylinder block and
the shell, or between the cylinder block and the shell, the
intermediate chamber communicates with the suction passage, wherein
the discharge chamber is located on the end plate side of the valve
unit; wherein the piston head includes a suction valve unit between
the compression chamber and the suction passage, wherein the
intermediate chamber forms the suction chamber.
4. The linear electric compressor according to claim 1, wherein the
housing further comprises an accommodation hole which is coaxial
with the cylinder bore and has the same diameter as that of the
cylinder bore, wherein the urging device is disposed between the
cylinder rod and the accommodation hole.
5. The linear electric compressor according to claim 4, wherein the
seat protrudes from inner surface of the housing into the
accommodation hole so as to receive the end of the urging
device.
6. A refrigerant circuit comprising: the linear electric compressor
according to; a condenser; an expansion valve; an evaporator; a
plurality of tubes connecting above components and through which
refrigerant gas flows; a power supply supplying electric power to
the coil of the linear electric compressor; a detecting device
detecting a state quantity of the linear electric compressor; and a
control device controlling the electric power that the power supply
supplies, based on the state of quantity detected by the detecting
device.
7. The refrigerant circuit according to claim 6, wherein the state
of quantity is a physical quantity influenced by a position of the
piston of the linear electric compressor.
8. The refrigerant circuit according to claim 7, wherein the
physical quantity is a pressure difference between first pressure
at first position and second pressure at second position in the
refrigerant circuit that is located downstream of the first
position.
9. The refrigerant circuit according to claim 8, wherein the
detecting device is provided in the tube, wherein the detecting
device including: a spool that is movable based on the pressure
difference; a moving permanent magnet fixed to the spool; and a
magnetic force detecting device detecting magnetic flux density of
the moving permanent magnet.
10. The refrigerant circuit according to claim 9, wherein the first
and the second positions are provided in the tube located between
the discharge chamber and the condenser, wherein a throttle is
provided between the first and the second positions.
11. The refrigerant circuit according to claim 9, wherein a bend is
provided between the first and the second positions.
12. The refrigerant circuit according to claim 7, wherein the
detecting device detects a position of the piston directly.
Description
BACKGROUND OF THE INVENTION
[0001] The present invention relates to a linear electric
compressor and also to a refrigerant circuit including the linear
electric compressor.
[0002] Japanese Patent No. 3953735 discloses a linear electric
compressor which includes a double-headed piston including a piston
rod and piston heads at the opposite ends of the piston rod and
compression chambers formed at the outer end of each piston head.
The linear electric compressor further includes permanent magnets
provided at positions corresponding to the center of the piston rod
of the double-headed piston and to each piston head thereof and
coils provided around the piston rod and each piston head. The
linear electric compressor still further includes a pair of springs
provided inside the double-headed piston.
[0003] By supplying electric power periodically to energize the
coils of the linear electric compressor of the above patent,
periodically variable electromagnetic force is generated around the
coils and the permanent magnets of the pistons are attracted toward
or repelled from the coils by the electromagnetic force.
Accordingly, the pistons reciprocate in cylinder bores. The pistons
reciprocate also by resonance of natural frequency of the springs.
The reciprocating movement of the pistons causes refrigerant gas to
be introduced from a suction chamber to a compression chamber,
compressed in the compression chamber and discharged into a
discharge chamber. Thus, the linear electric compressor can be
electrically controlled to compress refrigerant gas and used for an
air conditioner for an electric vehicle and the like.
[0004] Furthermore, this type of linear electric compressor can
compress refrigerant gas twice by a single reciprocating movement
of the piston and, therefore, the performance of compressing
refrigerant gas per unit time can be improved and the compressor be
made small as compared with a linear electric compressor having a
compression chamber only at one end of the piston.
[0005] However, the linear electric compressor of the above patent
requires a space in the piston for installing the springs.
Therefore, the outer diameter of the piston is increased and the
inner diameter of the cylinder bore needs to be designed
accordingly. This type of linear electric compressor has
limitations on downsizing.
[0006] The present invention is directed to providing a linear
electric compressor that can be made small while ensuring the
performance of compressing refrigerant gas per unit time and also a
refrigerant circuit having the linear electric compressor.
SUMMARY OF THE INVENTION
[0007] A refrigerant circuit includes a linear electric compressor
including a housing with a cylinder bore, a pair of end plates, a
valve unit, a piston, an urging device for urging the piston, a
coil generating electromagnetic force and a permanent magnet. The
permanent magnet cooperates with the urging device and the coil to
reciprocate the piston in the cylinder bore. The piston further
includes a piston rod and the urging device is provided around the
piston rod and a pair of piston heads integrally formed at opposite
ends of the piston rod. The diameter of the piston rod is smaller
than that of the piston head. The permanent magnet is provided on
the piston head and the coil surrounds the piston head. The housing
further includes a seat located between the pair of piston heads
and the urging device is provided between the seat and each of the
piston head.
[0008] Other aspects and advantages of the invention will become
apparent from the following description, taken in conjunction with
the accompanying drawings, illustrating by way of example the
principles of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] The features of the present invention that are believed to
be novel are set forth with particularity in the appended claims.
The invention together with objects and advantages thereof, may
best be understood by reference to the following description of the
presently preferred embodiments together with the accompanying
drawings in which:
[0010] FIG. 1 is a cross sectional view of a linear electric
compressor according to a first embodiment of the present
invention;
[0011] FIG. 2 is a schematic view of a refrigerant circuit using
the linear electric compressor of FIG. 1;
[0012] FIG. 3 is a partially enlarged cross sectional view of the
linear electric compressor of FIG. 1;
[0013] FIG. 4 is a schematic view showing coils and permanent
magnets of the linear electric compressor of FIG. 1;
[0014] FIG. 5 is a schematic view of a refrigerant circuit
according to a second embodiment of the present invention;
[0015] FIG. 6 is an enlarged cross sectional view showing a flow
sensor and tubes to which the flow sensor is mounted in the
refrigerant circuit of FIG. 5;
[0016] FIG. 7 is a schematic view of a refrigerant circuit
according to a third embodiment of the present invention; and
[0017] FIG. 8 is an enlarged cross sectional view showing the flow
sensor and tubes to which the flow sensor is mounted in the
refrigerant circuit of FIG. 7.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0018] The following will describe the linear electric compressor
and the refrigerant circuit according to the first through third
embodiments of the present invention with reference to FIGS. 1
through 8. The linear electric compressor 100 according to the
first embodiment and the refrigerant circuits 140, 200, 300
according to the first through the third embodiments, respectively,
are employed for an air conditioner for a hybrid vehicle or an
electric vehicle.
[0019] As shown in FIG. 1, the linear electric compressor 100
includes a first and a second cylinder blocks 1, 3, a shell 5 and a
center housing 7, which cooperate to form a housing 9 of the linear
electric compressor 100. The first and the second cylinder blocks
1, 3 have formed therein a first and a second cylinder bores 1A,
3A, respectively. The first and the second cylinder bores 1A, 3A
are designed so that they are coaxially formed and have the same
diameter.
[0020] The first and the second cylinder blocks 1, 3 have a first
and a second flanges 1B, 3B around the first and the second
cylinder bores 1A, 3A, respectively, which are housed in the shell
5 so that the first and the second flanges 1B, 3B are located at
the opposite ends of the shell 5. The center housing 7 is provided
in the shell 5 between the first and the second cylinder blocks 1,
3. The center housing 7 has formed therethrough in axial direction
thereof an accommodation hole 7A which is coaxial with the first
and the second cylinder bores 1A, 3A and the diameter of which is
substantially the same as those of the first and the second
cylinder bores 1A, 3A.
[0021] A first and a second end plates 11, 13 are joined to the
opposite ends of the shell 5 through a first and a second gaskets
10, 12, respectively. The first and the second end plates 11, 13
have formed therein recesses, respectively and a first and a second
valve plates 15, 17 are held between the first gasket 10 and the
first end plate 11 and between the second gasket 12 and the second
end plate 13, respectively. A first and a second discharge chambers
11A, 13A are formed by the recesses between the first and the
second end plates 11, 13 and the first and the second valve plates
15, 17, respectively. The first and the second end plates 11, 13
have formed therethrough a first and a second discharge ports 11B,
13B, respectively. The first and the second discharge chambers 11A,
13A are connected to tubes 101, 102 shown in FIG. 2 through the
first and the second discharge ports 11B, 13B, respectively. The
first and the second discharge chambers 11A, 13A form the discharge
chamber of the present invention.
[0022] As shown in FIG. 3, the first valve plate 15 has formed
therethrough a discharge port 15A. A reed type discharge valve 19
for opening and closing the discharge port 15A and a retainer 21
for regulating the opening of the discharge valve 19 are fixed by a
rivet 23 to the first valve plate 15 on the first discharge port
11B side. The first valve plate 15, the discharge valve 19, the
retainer 21 and the rivet 23 cooperate to form a first valve unit
25. Similarly, a second valve unit is formed on the second valve
plate 17 side. The first and the second valve units 25 are provided
between the first and the second cylinder bores 1A, 3A and the
first and the second end plates 11, 13, respectively.
[0023] As shown in FIG. 1, the first and the second cylinder bores
1A, 3A and the accommodation hole 7A receive therein a reciprocally
slidable piston 27. The piston 27 includes a piston rod 29 and a
first and a second piston heads 31, 33 which are integrally
provided with the piston rod 29 at the opposite ends of the piston
rod 29, respectively and slidable in the first and the second
cylinder bores 1A, 3A, respectively.
[0024] As shown in FIGS. 3 and 4, the first piston head 31 includes
a head 39, on outer surface of which permanent magnets 35, 37 are
fixed, and a first and a second spacers 41, 43 which are integrally
provided with the head 39 and form a space between the inner
surface of the first cylinder bore 1A and the outer surface of the
permanent magnets 35, 37.
[0025] The permanent magnets 35, 37 are ring shaped and use a
rare-earth magnet. North and south poles of the permanent magnet 35
are located on the outer surface thereof and the inner surface
thereof, respectively, and, on the other hand, south and north
poles of the permanent magnet 37 are located on the outer surface
thereof and the inner surface thereof, respectively. The polar
character of the permanent magnets 35, 37 may be reversed.
[0026] In installing the permanent magnets 37, 35, firstly the
second spacer 43 is press-fit on the head 39, the permanent magnets
37, 35 are press-fit on the outer surface of the head 39, and then
the first spacer 41 is press-fit on the outer surface of the head
39, as shown in FIG. 3. Thus, the permanent magnets 35, 37 are held
securely on the outer surface of the head 39 between the first and
the second spacers 41, 43. A compression chamber 45 is formed in
the first cylinder bore 1A by the space outward of the first spacer
41 of the first piston head 31.
[0027] As shown in FIG. 3, a suction port 39A is formed through the
head 39 for fluid communication between the inside of the head 39
and the compression chamber 45. The first spacer 41 has formed
therethrough a valve hole 41A that is communicable with the suction
port 39A, and houses therein a float-type suction valve 47. The
valve hole 41A has a stop 41B formed on the side thereof adjacent
to the compression chamber 45. The suction valve 47 is formed in
the outer periphery thereof with a plurality of engagement plates
47A that are brought into contact with the stop 41B when the
suction port 39A is opened. A cutout 47B is formed between any two
adjacent engagement plates 47A.
[0028] As shown in FIG. 1, the first and the second piston heads
31, 33 are press-fit on the opposite ends of the piston rod 29. The
diameter of the piston rod 29 is smaller than those of the first
and the second piston heads 31, 33. The piston rod 29 has formed
therethrough in axial direction thereof a suction passage 29A. The
suction passage 29A includes also radially extending passages in
the center of the piston rod 29 so as to open at the outer
peripheral surface of the piston rod 29. As shown in FIG. 3, the
suction passage 29A communicates with the suction port 39A of the
first piston head 31. The suction passage 29A, the suction port
39A, the suction valve 47 and the first spacer 41 cooperate to form
a suction valve unit 50. The suction valve unit on the second
piston head 33 side has substantially the same structure.
[0029] As shown in FIG. 1, the center housing 7 has formed on the
inner peripheral surface and at the center thereof a seat 7B that
protrudes into the accommodation hole 7A at the center between the
opposite outer end surfaces of the first and the second cylinder
blocks 1, 3. It can be also said that the seat 7B is located
between the first and the second piston heads 31, 33. The space
between the inner peripheral surface of the accommodation hole 7A
and the outer peripheral surface of the piston rod 29 forms a
spring chamber 7C communicating with the suction passage 29A. The
spring chamber 7C houses therein a first and a second coil springs
49, 51 as an urging device for urging the piston 27.
[0030] The first coil spring 49 is preloaded with one end thereof
in contact with the seat 7B and the other end thereof in contact
with the second spacer 43 of the first piston head 31.
[0031] The center housing 7 and the shell 5 forms therebetween an
intermediate chamber 53. The intermediate chamber 53 may be
provided in either the center housing 7 or the shell 5. A
communication hole 7D that connects the intermediate chamber 53 and
the spring chamber 7C is formed in the center housing 7. The
intermediate chamber 53 is communicable with the first and the
second cylinder bores 1A, 3A through the suction passage 29A.
Combination of the intermediate chamber 53 and the spring chamber
7C forms a suction chamber 55. An inlet 5A is formed through the
shell 5. The suction chamber 55 is connected to a tube 103 shown in
FIG. 2 through the inlet 5A. A cover 57 is fixed to the shell 5 for
closing the intermediate chamber 53. Terminals (not shown) that are
connected to coils 63A, 63B, 65A, 65B as will be described
hereinafter are fixed to the cover 57.
[0032] The coils 63A, 63B and 65A, 65B are provided between the
shell 5 and the first and the second cylinder blocks 1, 3, with the
coils 63A, 63B and 65A, 65B held by a first and a second support
members 59, 61, respectively. The coils 63A, 63B and 65A, 65B are
disposed so as to surround the first and the second piston heads
31, 33, respectively. The first and the second cylinder blocks 1, 3
and the first and the second support members 59, 61 are made of a
magnetic material. Alternatively, the first and the second cylinder
blocks 1, 3 may be made of a nonmagnetic material
[0033] As shown in FIG. 2, the tubes 101, 102 connect the linear
electric compressor 100 to a tube 104, which is in turn connected
to a condenser 105. The condenser 105 is connected to an expansion
valve 107 and an evaporator 108 through a tube 106. The evaporator
108 is connected to a tube 103. The terminals in the intermediate
chamber 53 for the coils 63A, 63B, 65A, 65B are connected to a
power supply 110 through a lead wire 109. The power supply 110 is
electrically controlled. The above components cooperate to form the
refrigerant circuit 140.
[0034] The power supply 110 supplies electric power to energize the
coils 63A, 63B, 65A, 65B of the linear electric compressor 100
periodically thereby to generate periodically variable
electromagnetic force around the coils 63A, 63B, 65A, 65B.
Referring to FIG. 4, when the coil 63A attracts the permanent
magnet 35 of the first piston head 31, magnetic repulsion is
generated between the coil 63B and the permanent magnet 37 of the
first piston head 31. On the other hand, when magnetic repulsion is
generated between the coil 63A and the permanent magnet 35 of the
first piston head 31, the coil 63B attracts the permanent magnet 37
of the first piston head 31. Thus, the piston 27 is caused to
reciprocate in the first and the second cylinder bores 1A, 3A. The
piston 27 also reciprocates by resonance due to natural frequencies
of the first and the second coil springs 49, 51.
[0035] Strokes of suction, compression and discharge of refrigerant
gas are accomplished by the reciprocating movement of the piston
27. The following will describe the operation of the linear
electric compressor. The description will focus on the movement of
the first piston head 31. As shown in FIG. 3, when the first piston
head 31 is in the suction stroke, the pressure in the compression
chamber 45 is reduced and, accordingly, the suction valve 47 moves
within the valve hole 41A so as to open the suction port 39A.
Therefore, refrigerant gas in the suction chamber 55 flows from the
suction port 39A into the compression chamber 45 through clearances
between the cutouts 47B of the suction valve 47 and the stop 41B.
Then, the discharge port 15A is closed by the discharge valve
19.
[0036] When the first piston head 31 begins its compression stroke,
the suction valve 47 moves within the valve hole 41A so as to close
the suction port 39A. Accordingly, the pressure in the compression
chamber 45 is increased thereby to open the discharge valve 19.
Thus, the first piston head 31 begins its discharge stroke and the
compressed refrigerant gas is discharged into the first discharge
chamber 11A through the discharge port 15A. Though the refrigerant
gas in the first discharge chamber 11A is hot, the first gasket 10
provided between the first end plate 11 and the first cylinder
block 1 prevents the piston 27 from being exposed directly to the
first discharge chamber 11A. Therefore, the piston 27 is
unsusceptible to the heat of the refrigerant gas in the first
discharge chamber 11A. The same is true of the second piston head
33 side when the second piston head 33 is in the compression
stroke.
[0037] Referring to FIG. 2, refrigerant gas flowing out from the
evaporator 108 through the tube 103 flows into the compression
chamber 45 through the suction chamber 55. Refrigerant gas is
compressed in the compression chamber 45 and then discharged into
the first and the second discharge chambers 11A, 13A. Refrigerant
gas in the first and the second discharge chambers 11A, 13A flows
out therefrom through the tubes 101, 102 to the condenser 105, the
expansion valve 107 and the evaporator 108. The linear electric
compressor 100 which is operable to compress refrigerant gas by
electrical control may be used advantageously for air conditioning
for an electric vehicle and the like. For example, when the engine
of a hybrid vehicle is turned off while the hybrid vehicle is at a
stop, comfortable air conditioning can be achieved by the
electrically controlled linear electric compressor 100.
[0038] The linear electric compressor 100 of the present embodiment
can compress refrigerant gas twice by a single reciprocating
movement of the piston 27, thus improving the performance of
compressing refrigerant gas per unit time as compared with a linear
electric compressor having a compression chamber only at one end of
a piston rod.
[0039] Furthermore, the linear electric compressor 100 includes the
first and the second coil springs 49, 51 in the center of the
double-headed piston 27. The diameter of the piston rod 29 is
smaller than that of the first and the second piston heads 31, 33.
The first and the second coil springs 49, 51 are provided in the
spring chamber 7C, the diameter of which is substantially the same
as that of the first and the second cylinder bores 1A, 3A.
Therefore, the linear electric compressor 100 dispenses with an
urging device in the compression chamber 45 and the compression
chamber 45 can be made large. Since the diameter of the first and
the second coil springs 49, 51 is not larger than that of the first
and the second piston heads 31, 33, the inner diameter of the first
and the second cylinder bores 1A, 3A and the accommodation hole 7A
of the center housing 7 can be designed in accordance with the
outer diameter of the first and the second piston heads 31, 33.
[0040] Therefore, the linear electric compressor 100 can be made
smaller while achieving high performance of compressing refrigerant
gas per unit time. The refrigerant circuit 140 employing the linear
electric compressor 100 can be also made small while maintaining
high compression performance.
[0041] In the linear electric compressor 100 of the present
embodiment wherein the permanent magnets 35, 37 are provided in the
first and the second piston heads 31, 33 and the coils 63A, 63B and
65A, 65B are provided around the first and the second piston heads
31, 33, respectively, the electromagnetic force and the permanent
magnets 35, 37 operate each other at the opposite ends of the
double-headed piston 27. Therefore, it is hard for the ends of the
piston 27 to deflect in radial direction of the piston 27, which
makes it difficult for the first and the second piston heads 31, 33
to interfere with the inner surface of the first and the second
cylinder bores 1A, 3A, respectively.
[0042] Since the housing 9 of the linear electric compressor 100
includes the first and the second cylinder blocks 1, 3 and the
shell 5, it is easy to install the coils 63A, 63B and 65A, 65B
between the shell 5 and the respective first and the second
cylinder blocks 1, 3, thus facilitating manufacturing of the linear
electric compressor 100.
[0043] The intermediate chamber 53 of the linear electric
compressor 100 is formed by the shell 5 and the center housing 7
between the first and the second cylinder blocks 1, 3. The first
and the second discharge chambers 11A, 13A are formed in the first
and the second end plates 11, 13 by providing the valve units 25,
respectively, and the suction valve units 50 are provided in the
first and the second piston heads 31, 33, respectively. Moreover,
the spring chamber 7C and the suction passage 29A both serving also
as a part of the suction chamber 55 are formed in the piston 27.
This structure makes it possible for the linear electric compressor
100 to be made small and light while achieving high performance of
compressing refrigerant gas.
[0044] Now referring to FIG. 5, the refrigerant circuit 200
according to the second embodiment is made by modifying a part of
the refrigerant circuit 140 (FIG. 2) according to the first
embodiment. As shown in FIG. 5, the tube 104 of the first
embodiment is replaced by a tube 150. The tube 150 is provided
between the condenser 105 and the respective first and the second
discharge chambers 11A, 13A (FIG. 1). The refrigerant circuit 200
includes a flow sensor 111 as a detecting device and a control
device 112.
[0045] As shown in FIG. 6, a throttle 70 is provided inside the
tube 150. Reference symbols 150A and 150B designate first and
second positions in the refrigerant circuit 200 that are upstream
and downstream of the throttle 70, respectively, with respect to
the flowing direction of refrigerant gas in the tube 150 indicated
by arrow. An upstream tube 120 is connected to the first position
150A and a downstream tube 121 is connected to the second position
150B, respectively.
[0046] The flow sensor 111 is provided in the tube 150 for
detecting a pressure difference between the first pressure P1 and
the second pressure P2 of refrigerant gas flowing through the first
position 150A and the second position 150B, respectively. The flow
sensor 111 includes a sensor body 71 and a hall device 73 as a
magnetic force detecting device.
[0047] The sensor body 71 houses a spool 75 that is movable in
vertical direction. A moving permanent magnet 77 is fixed to the
spool 75. A spring seat 79 is fixed to lower end of the sensor body
71 and a first spring 81 is provided between the spring seat 79 and
the spool 75 for urging the spool 75 upward as viewed in the
drawing. A second spring 83 is provided between upper inner surface
of the sensor body 71 and the spool 75 for urging the spool 75
downward.
[0048] The upstream tube 120 is connected to the sensor body 71 at
a position that is higher than that of the spool 75 and the
downstream tube 121 is connected to the spring seat 79, as shown in
FIG. 6. When the second pressure P2 is higher than the first
pressure P1, the spool 75 is moved upward against the urging force
of the second spring 83 in the sensor body 71. When the second
pressure P2 is lower than the first pressure P1, on the other hand,
the spool 75 is moved downward against the urging force of the
first spring 81 in the sensor body 71.
[0049] The hail device 73 is fixed to top surface of the sensor
body 71. The hall device 73 detects the magnetic flux density that
is variable in accordance with the vertical movement of the spool
75 with the moving permanent magnet 77 toward and away from the
hall device 73. As shown in FIG. 5, the hall device 73 is
electrically connected to the control device 112 through a first
control circuit 130. The hall device 73 generates to the control
device 112 a control signal representing the detected magnetic flux
density.
[0050] The control device 112 includes a stroke computing part 113
and a voltage-frequency controlling part 114. The control device
112 is electrically connected to the power supply 110 through a
second control circuit 131.
[0051] The stroke computing part 113 of the control device 112
computes the present position of the piston 27 (FIG. 1) based on
the control signal received from the hall device 73, i.e., the flow
rate of refrigerant gas flowing through the tube 150. The position
of the piston 27 represents to the state quantity of the linear
electric compressor 100. The state quantity of the linear electric
compressor 100 can be a physical quantity influenced by the current
position of the piston 27 as indicated above, a pressure or a
temperature of refrigerant gas being discharged from the linear
electric compressor 100 or flowing thereinto, or a combination of
these state quantities. In other words, the physical quantity can
be determined indirectly by measuring the flow rate of refrigerant
gas flowing through the linear electric compressor 100 or any tube
in the refrigerant circuit 200 with the aid of a flow meter. In the
case of the present embodiment, the physical quantity should
preferably be the pressure difference between the first pressure P1
in the first position 150A and the second pressure P2 in the second
position 1508 that is located downstream of the first position
150A. The stroke computing part 113 determines the current position
of the piston 27 by backward calculation of the drive frequency of
the piston 27. The stroke computing part 113 shown in FIG. 5
generates to the voltage-frequency controlling part 114 a control
signal representing the state quantity of the linear electric
compressor 100.
[0052] The voltage-frequency controlling part 114 of the control
device 112 controls the voltage, the current and the current
frequency of electric power supplied from the power supply 110 to
the linear electric compressor 100, based on the control signal
that is received from the stroke computing part 113. The
voltage-frequency controlling part 114 can control independently
the voltage, the current and the current frequency of electric
power which is supplied from the power supply 110 to the linear
electric compressor 100, i.e., the voltage, the current and the
cycle length of current of electric power which is supplied to
coils 63A, 63B, 65A, 65B. The same reference numerals are used for
the common elements or components of the refrigerant circuit 200
and the refrigerant circuit 140 according to the first embodiment,
and the description of such elements or components for the second
embodiment will be omitted.
[0053] The power supply 110 in the refrigerant circuit 200
according to the second embodiment supplies electric power to the
linear electric compressor 100 based on the state quantity. The
state quantity of the linear electric compressor 100 in the
refrigerant circuit 200 is determined by detecting the physical
quantity influenced by the position of the piston 27 (FIG. 1) in
the linear electric compressor 100. Thus, the electric power
supplied to the linear electric compressor 100 is controlled based
on the state quantity. Not only when the voltage and the current
which are supplied to the coils 63A, 63B, 65A, 65B, respectively
increase but also when the periodic voltage and current are kept
constant, the thermal load and the pressure of refrigerant gas in
the compression chamber 45 of the linear electric compressor 100
changes. Then, the distance of reciprocating movement of the piston
27, i.e., the piston stroke, caused by the electromagnetic force
generated by the predetermined electric power also changes. For
example, when the thermal load is low and the pressure of
refrigerant gas in the compression chamber 45 decreases, the first
and the second pistons may collide against their corresponding
valve units and the collision causes noise and vibration in the
linear electric compressor 100. This may decrease the durability of
the linear electric compressor 100. Therefore, when the thermal
load decreases and the pressure of the refrigerant gas in the
compression chamber 45 of the linear electric compressor 100 also
decreases, the collision of the first and the second piston heads
31, 33 against the first and the second valve plates 15, 17,
respectively, can be prevented by the refrigerant circuit 200
according to the second embodiment having the above-mentioned
control based on the state quantity. Accordingly, the durability of
the linear electric compressor 100 in the refrigerant circuit 200
can be also improved.
[0054] The flow sensor 111 in the refrigerant circuit 200 can
detects the pressure difference between the first pressure P1 and
the second pressure P2 in the tube 150 by detecting the change of
the magnetic flux density. Therefore, the flow rate of refrigerant
gas flowing through the tube 150 can be detected precisely at a
moderate cost. The flow sensor 111 which is provided in the tube
150 away from the linear electric compressor 100 is free from the
influence of the magnetic flux generated by the coils 63A, 63B,
65A, 65B of the linear electric compressor 100.
[0055] In the refrigerant circuit 200 according to the second
embodiment, the throttle 70 is provided in the tube 150 in which
high-pressure refrigerant gas flows. Therefore, pressure loss of
refrigerant gas incurred in the throttle 70 does not decrease the
performance of the refrigerant circuit 200. The other advantageous
effects are the same as those in the refrigerant circuit according
to the first embodiment.
[0056] Referring to FIG. 7, the refrigerant circuit 300 according
to the third embodiment differs from the refrigerant circuit 200 of
the second embodiment in that the flow sensor 111 is provided in a
bend 90 of the tube 103. Accordingly, in the refrigerant circuit
300 of the third embodiment, the tube 104 that is used in the
refrigerant circuit 140 of the first embodiment is used in place of
the tube 150 in the refrigerant circuit 200 of the second
embodiment. No throttle such as 70 is provided in the refrigerant
circuit 300.
[0057] Referring to FIG. 8, reference symbols 130A, 130B designate
first and second positions in the tube 103 of the refrigerant
circuit 300 that are upstream and downstream of the bend 90,
respectively, with respect to the flowing direction of refrigerant
gas in the tube 103 indicated by bent arrow. The upstream tube 120
is connected to the first position 103A and the downstream tube 121
is connected to the second position 1038. The same reference
numerals are used for the common elements or components of the
refrigerant circuits 200 and 300 according to the second and the
third embodiments, and the description of such elements or
components for the third embodiment will be omitted.
[0058] The flow sensor 111 in the refrigerant circuit 300 can
detect the pressure difference between the first pressure P1 and
the second pressure P2 of refrigerant gas flowing through the first
position 103A and the second position 103B, respectively, based on
the flow passage resistance caused by the bend 90 through which
refrigerant gas flows. By installing the flow sensor 111 to the
bend 90 of the tube 103 which is inevitably formed for mounting of
the refrigerant circuit 300 to the vehicle, the flow rate of
refrigerant gas flowing through the tube 103 is detected easily and
efficiently. The bend 90 may not necessarily be formed by bending
the tube 103 at almost a right angle. As long as a resistance is
generated against the refrigerant gas flowing through the bend 90,
the bend 90 may be formed by bending the tube 103 at any angle
other than a right angle. Additionally, the bend 90 may be provided
at a position in which high-pressure refrigerant gas flows, e.g.,
at a position anywhere in the tube 104. The other advantageous
effects are the same as those in the refrigerant circuit 200
according to the second embodiment.
[0059] The present invention is not limited to the first through
third embodiments, but may be modified within the effects of the
present invention.
[0060] The linear electric compressor 100 according to the first
embodiment is used alone, but it may be used in combination with
any other compressor. This is also applicable to the second and the
third embodiments.
[0061] In the first through third embodiments, the first and the
second discharge chambers 11A, 13A are formed on the first and the
second end plate 11, 13 sides, respectively and a suction chamber
55 is formed in the piston 27. However, suction chambers may be
formed on the first and the second end plate 11, 13 sides,
respectively and a discharge chamber may be formed in the piston
27.
[0062] The first and the second spacers 41, 43 may be made of
fluororesin such as PTFE. In this case, the piston 27 reciprocates
suitably in the first and the second cylinder bores 1A, 3A.
[0063] The suction valve unit 50 may be of a reed type.
[0064] As the detecting device for detecting the piston 27, any
suitable sensor may be used, including a position sensor using
laser or magnetic flux, a differential transformer and a proximity
switch.
[0065] A plurality of flow sensors 111 may be provided in the tubes
101-104 (150), 106. For detecting the state of refrigerant gas
flowing through the linear electric compressor 100 and the tubes
101-104 (105), 106 with an increased accuracy, a pressure sensor
and a temperature sensor may be used in place of the flow sensor
111. In this case, the stroke computing part 113 can compute the
physical quantity more accurately.
[0066] The refrigerant circuit according to the present invention
may be used for a hybrid vehicle and an electric vehicle using an
electric motor. It is also applicable to a vehicle equipped with an
engine.
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