[0001] This relates to a compressor and, in particular, to a compressor including refrigerant
bypasses, and a refrigerating apparatus including such a compressor.
[0002] A compressor is a component of a refrigerating cycle that compresses refrigerant
gas. Types of compressors may include, for example, a reciprocating compressor in
which a refrigerant is compressed by a piston and crank shaft, a rotary compressor
in which refrigerant gas is compressed by a rotor and vanes, or a scroll compressor
in which refrigerant gas is compressed in compression chambers formed by two inter-engaged
scrolls, one rotating relative to the other. The scroll compressor may exhibit higher
efficiency and lower vibration and noise compared to the reciprocating compressor
or the rotary compressor.
[0003] WO 2007/050292 and
EP0725255 disclose scroll compressors according to the preamble of claim 1.
EP0725255 also discloses partial features of the characterising portion and can be considered
as closest prior art.
[0004] According to claim 1 the invention provides a scroll compressor, comprising a casing,
a fixed scroll fixed to an interior of the casing, an orbiting scroll movably engaged
with the fixed scroll so as to form compression chambers therebetween that are consecutively
moved as the orbiting scroll moves relative to the fixed scroll, a back pressure chamber
formed at a bearing surface formed between the fixed and orbiting scrolls, wherein
the back pressure chamber is configured to support a position of the orbiting scroll
against the fixed scroll; a first passage formed in the fixed scroll and configured
to guide refrigerant compressed in the compression chambers back into the back pressure
chamber; and a second passage formed at the fixed scroll and configured to guide refrigerant
into the compression chambers from a refrigerating cycle , wherein an angle between
the first passage and the second passage is greater than approximately 30° in a circumferential
direction along the wrap of the scroll, and wherein an outlet of the second passage
is closer to a discharge side of the compression chambers than an outlet of the first
passage.
[0005] The embodiments will be described in detail with reference to the following drawings
in which like reference numerals refer to like elements wherein:
FIG. 1 is a longitudinal sectional view of an upper portion of a scroll compressor
in accordance with an embodiment as broadly described herein;
FIG. 2 is a cut-away view of a compression unit of the scroll compressor shown in
FIG. 1;
FIG. 3 is a view taken along the line "II-II" of FIG. 2;
FIG. 4 is an enlarged longitudinal sectional view of a back pressure passage shown
in FIG. 3;
FIG. 5 is an enlarged longitudinal sectional view of an injection passage shown in
FIG. 3;
FIG. 6 is a view taken along the line "I-I" of FIG. 2;
FIG. 7 is an enlarged view of a phase difference between the back pressure passage
and the injection passage shown in FIG. 6;
FIG. 8 is a schematic view of a refrigerating cycle including a scroll compressor
as embodied and broadly described herein;
FIGS. 9A and 9B are graphs of pressure variation inside the back pressure chamber
of the scroll compressor based on the phase difference between the back pressure passage
and the injection passage in the refrigerating cycle shown in FIG. 8; and
FIG. 10 is a perspective view of an exemplary air conditioner having the scroll compressor
shown in FIG. 1.
[0006] Scroll compressors may be divided into low pressure type scroll compressors and high
pressure type scroll compressors based on how refrigerant is supplied into its compression
chambers. That is, in a low pressure type scroll compressor, refrigerant may be indirectly
drawn into a compression chamber via an inner space of a casing, the inner space of
the casing being divided into a suction space and a discharge space. In a high pressure
type scroll compressor, refrigerant may be supplied directly into a compression chamber
without flowing through the inner space of the casing, and may then be discharged
into the inner space of the casing, such that a majority of the inner space of the
casing defines a discharge space.
[0007] Scroll compressors may also be divided into a tip seal type scroll compressor and
a back pressure type scroll compressor based on a sealing mechanism used in the compression
chamber. That is, in a tip seal mechanism, a tip chamber disposed at an upper end
of wraps of each scroll is raised so as to be closely adhered to a plate portion of
a facing scroll. In a back pressure mechanism, a back pressure chamber is formed at
a rear surface of one scroll and intermediate pressure oil or refrigerant is induced
into the back pressure chamber to render the scroll closely adhered to an opposite
scroll due to pressure applied by the back pressure chamber. Typically, a tip seal
mechanism is used with a low pressure type scroll compressor, and a back pressure
mechanism is used with a high pressure type scroll compressor.
[0008] Scroll compressors may also be divided into a fixed capacity type and a variable
capacity type based on how refrigerant circulates therethrough. That is, in a fixed
capacity type scroll compressor substantially all of the refrigerant discharged therefrom
circulates through a closed loop refrigerating cycle, i.e., sequentially through the
compressor, a condenser, an expansion apparatus and an evaporator and then back into
the compressor. In a variable capacity type compressor, a portion of the refrigerant
discharged therefrom is bypassed at a middle portion of a refrigerating cycle and
introduced into an intermediate compression chamber of the compressor, while the remainder
of the refrigerant sequentially flows through the devices of a closed loop refrigerating
cycle and is introduced back into the compressor.
[0009] In a variable capacity type scroll compressor having a back pressure passage through
which an intermediate compression chamber communicates with a back pressure chamber
and an injection passage through which an outlet of the condenser communicates with
the intermediate compression chamber of the compressor, an interval between the back
pressure passage and the injection passage may adversely affect the performance of
the compressor. That is, since a refrigerant at intermediate pressure within the refrigerating
cycle is introduced into the intermediate compression chamber via the injection passage,
if the back pressure passage and the injection passage are too close to a proceeding
direction of a compression chamber, the intermediate pressure refrigerant in the injection
passage may leak into the back pressure chamber via the back pressure passage, thereby
increasing the pressure inside the back pressure chamber to an unacceptable level,
thus not properly maintaining pressure of the back pressure chamber. As a result,
a scroll supported by the pressure of the back pressure chamber may be excessively
adhered to or pressed against the opposite scroll, thereby incurring frictional loss
and abrasion of the wraps, and degrading reliability and performance of the compressor.
[0010] As shown in FIG. 1, a high pressure type scroll compressor as embodied and broadly
described herein may include a casing 10 that forms a hermetic inner space, a main
frame 20 and a sub frame (not shown in FIG. 1) respectively positioned in an upper
inner space and a lower inner space of the casing 10, a driving motor 30 mounted between
the main frame 20 and the sub frame for generating a rotational force, a fixed scroll
40 fixed to an upper surface of the main frame 20 and directly coupled to a gas suction
pipe SP, an orbiting scroll 50 positioned on the upper surface of the main frame 20
so as to form compression chambers P through its engagement with the fixed scroll
40, and an Oldham's ring installed between the orbiting scroll 50 and the main frame
20 so that the orbiting scroll 50 orbits without being rotated.
[0011] The hermetic inner space of the casing 10 may be divided into an upper space S1 and
a lower space S2 by the main frame 20 and the fixed scroll 40 so that both the upper
and lower spaces S1 and S2 are maintained at a high pressure. A bottom portion of
the lower space S2 of the casing 10 may be filled with oil for lubrication of the
friction components of the compressor. The gas suction pipe SP may penetrate the outer
wall of the casing 10 so as to communicate with the upper space S1 of the casing 10,
while a gas discharge pipe DP communicates with the lower space S2 of the casing 10.
[0012] A shaft accommodation hole 21 may be formed through a center of the main frame 20,
and an oil pocket 22 in which oil drawn up through an oil passage 32a of a driving
shaft 32 may be formed at an upper end of the shaft accommodation hole 21. A back
pressure groove 23 may be formed at an edge of the upper surface of the main frame
20 so as to create a back pressure chamber S3 having an intermediate pressure that
is generated when a portion of refrigerant and oil drawn in are mixed together. A
sealing groove may be formed in an annular shape within the back pressure groove 23
to receive a sealing member 60 therein such that oil collected in the oil pocket 22
may be maintained at a high pressure. The back pressure chamber S3 may be defined
by a combination of the back pressure groove 23 of the main frame 20, a plate portion
41 of the fixed scroll 40 and a plate portion 51 of the orbiting scroll 50.
[0013] The driving motor 30 may include a stator secured to the inside of the casing 10
and having a coil 31 to which external power is supplied, a rotor disposed within
the stator 31 with a predetermined air gap therebetween so as to rotate by interaction
with the stator, and a driving shaft 32 coupled to the rotor by, for example, a shrink
fitting, for transferring the rotational force of the driving motor 30 to the orbiting
scroll 50. An oil passage 32a may be formed through the driving shaft 32 in a longitudinal
direction of the shaft 32, and an oil pump may be installed at a lower end of the
oil passage 32a to pump oil from the bottom of the casing 10 into the oil passage
32a.
[0014] The fixed scroll 40 may include fixed wraps 42 spirally formed at a lower surface
of the plate portion 41 so as to form a pair of compression chambers P. An intake
port 43 in direct communication with the gas suction pipe SP may be formed at a side
surface of the plate portion 41, and a discharge port 44 through which a compressed
refrigerant is discharged up to the upper space S1 of the casing 10 may be formed
at a center of the upper surface of the plate portion 41. A back pressure passage
110 that defines a first passage between the compression chambers P and the back pressure
chamber S3 is formed between the wraps 42 forming the compression chambers P at a
lower surface of the plate portion 41, namely, at a surface thereof that defines a
thrust bearing surface together with the orbiting scroll 50.
[0015] The backpressure passage 110, as shown in FIGS. 2 to 4, may include a first back
pressure hole 111 that communicates with the back pressure chamber S3, a second back
pressure hole 112 that communicates with the compression chamber P, and a third back
pressure hole 113 that provides for communication between the first back pressure
hole 111 and the second back pressure hole 112. A communication groove 114 may be
formed at an end of the first back pressure hole 111, namely, at a surface facing
the back pressure groove 23, to provide for communication between the first back pressure
hole 111 and the back pressure groove 23. The communication groove 114 may be radially
formed and have a long, substantially rectangular shape such that its width is greater
than that of the first back pressure hole 111. Diameters d1, d2 and d3 of the back
pressure holes 111, 112 and 113, respectively maybe approximately the same so as to
minimize flow resistance.
[0016] The first, second and third back pressure holes 111, 112 and 113 may define one passage
that alternately communicates with the pair of compression chambers P. That is, the
second back pressure hole 112 may be located between adjacent fixed wraps 42, and
the diameter d2 of the second back pressure hole 112 may be less than a thickness
t of the wrap 52 of the orbiting scroll 50, as shown in FIG. 4 so as to prevent refrigerant
leakage from an inner compression chamber P to an outer compression chamber P due
to a pressure difference.
[0017] A blocking member 115 may be coupled to the third back pressure hole 113. For example,
in the embodiment shown in FIG. 4, the blocking member 115 may be inserted into an
external end of the third back pressure hole 113 by a predetermined depth so as to
isolate the third back pressure hole 113 from the inner space of the casing 10. In
certain embodiments, the blocking member 115 may be formed of a comparatively elastic
non-ferrous metal so as to be hermetically press-fitted within the external end of
the third bypass hole 113. Alternatively, as shown in FIGS. 3 and 4, the blocking
member 115 may be a metallic bolt that is threadly coupled to a predetermined depth
into the external end of the third bypass hole 113. When using such a metallic bolt,
a sealing washer 116 maybe hermetically inserted at a head portion of the metallic
bolt for coupling.
[0018] As shown in FIG. 1, the orbiting scroll 50 may include orbiting wraps 52 spirally
formed on an upper surface of a plate portion 51 so as to form a pair of compression
chambers P together with the fixed wraps 42 of the fixed scroll 40. A boss portion
53 may extend from a central portion of a lower surface of the plate portion 51 and
be coupled to the driving shaft 32 so as to receive a driving force from the driving
motor 30.
[0019] In certain embodiments, the fixed wrap 42 and the orbiting wrap 52 may be symmetrically
formed with substantially the same wrap length. In certain embodiments, they may be
symmetrically formed with different wrap lengths. For example, the orbiting wrap 52
may be approximately 180° longer than the fixed wrap 42. Other arrangements may also
be appropriate.
[0020] During operation, when power is applied to the driving motor 30, the driving shaft
32 rotates together with the rotor to transfer a rotational force to the orbiting
scroll 50. The orbiting scroll 50 performs an orbiting motion by an eccentric distance
on the upper surface of the main frame 20 due to the Oldham's ring, thereby forming
a pair of compression chambers P which are consecutively moved between the fixed wrap
42 of the fixed scroll 40 and the orbiting wrap 52 of the orbiting wrap 50. The volumes
of the compression chambers P are decreased as are moved toward the center in response
to the consecutive orbiting motion of the orbiting scroll 50, thereby compressing
refrigerant therein.
[0021] Simultaneously, an oil pump provided at the lower end of the driving shaft 32 pumps
oil contained in the casing 10 up via the oil passage 32a of the driving shaft 32.
A portion of the oil is supplied into the shaft accommodation hole 21 of the main
frame 20, and a portion of the oil is dispersed at the upper end of the driving shaft
32 so as to be introduced into the back pressure chamber S3 of the main frame 20.
The oil introduced into the back pressure chamber S3 supports the orbiting scroll
50, which is accordingly raised upward the fixed scroll 40. Hence, the fixed wraps
42 and the orbiting wraps 52 are closely adhered to the corresponding plate portions
51 and 41, respectively, thereby sealing the compression chambers P.
[0022] In this state, refrigerant is compressed by the continuous orbiting motion of the
orbiting scroll 50. The compressed refrigerant partially flows into the back pressure
chamber S3 via the back pressure passage 110, so that the pressure within the back
pressure chamber S3 may be maintained at a predetermined level. Although only one
outlet of the back pressure passage 110, namely, the second back pressure hole 112,
is provided, the second back pressure hole 112 alternately communicates with both
compression chambers P as the orbiting scroll 50 orbits, allowing oil to be uniformly
supplied into each compression chamber P via the back pressure passage 110.
[0023] In a variable capacity type compressor, refrigerant may be reintroduced into an intermediate
compression chamber of the compressor at a middle portion of a refrigerating cycle,
namely, from an outlet of a condenser, so as to increase an amount of refrigerant
to be compressed, resulting in an increase in the compression capacity of the compressor.
[0024] For example, as shown in Fig. 8, an injection pipe 6 may diverge at a middle portion
of a refrigerant pipe 5 that connects a condenser 2 and an expansion apparatus 3 of
the refrigerating cycle, namely, at an outlet of the condenser 2. The injection pipe
6 may be connected to an injection passage 120 that forms a second passage at the
fixed scroll 40 of the scroll compressor 1 shown in FIGS. 1 and 2. A bypass valve
7 for controlling the flow of refrigerant through the injection pipe 6 may be installed
at a middle portion of the injection pipe 6 or at an area where the injection pipe
6 diverges from the refrigerant pipe 5.
[0025] The injection passage 120, as shown in FIGS. 2, 3 and 5, includes a first injection
hole 121 formed in a radial direction at a predetermined depth in the fixed scroll
40, and a second injection hole 122 that extends in a shaft direction from an end
portion of the first injection hole 121 through the intermediate compression chamber.
[0026] Depending on the position of the second injection hole 122, refrigerant injected
therethrough from the middle portion of the refrigerating cycle may leak into the
back pressure chamber S3, possibly degrading compression performance. In order to
enhance performance of the compressor, specific positioning of the injection passage
120 with respect to the back pressure passage 110, and more particularly, the second
back pressure hole 112 of the back pressure passage 110 and the second injection passage
122 of the injection passage 120, maybe established.
[0027] To this end, the second injection hole 122 of the injection passage 120 is formed,
as shown in FIGS. 6 and 7, closer to the discharge side of the compression chamber
than the second back pressure hole 112 of the back pressure passage 110. More particularly,
the second injection hole 122 is formed so that an angle at which a refrigerant starts
to be injected into the intermediate compression chamber P and an angle at which the
refrigerant within the intermediate compressor chamber starts to be introduced into
the back pressure chamber S3 is greater than approximately 30°. Consequently, leakage
of the refrigerant injected into the intermediate compression chamber via the injection
passage 120 into the back pressure passage 110 is prevented. The greater the phase
difference between the second back pressure passage 112 of the back pressure passage
110 and the second injection passage 122 of the injection passage 120, the greater
the leakage prevention.
[0028] A diameter 24 of the second injection hole 122 may be substantially the same as a
diameter of the second back pressure hole 112, so as to smoothly control the amount
of refrigerant injected. The diameter d4 of the second injection hole 122 may be less
than a thickness t of the orbiting wrap 52 of the orbiting scroll 50 so as to prevent
a refrigerant injected via the injection passage 120 from being leaked into both the
compression chambers P due to the injection passage 120 communicating with the compression
chambers P.
[0029] A temperature of the refrigerant injected into the intermediate compression chamber
may be lower than a temperature at the outlet of the condenser 2 but higher than a
temperature at a suction side of the compression chamber P, so as to increase the
amount of the refrigerant to be injected. That is, as shown in FIG. 8, after a refrigerant
discharged from the compressor 1 flows through the condenser 2, part of the refrigerant
is bypassed into the injection pipe 6 at the outlet of the condenser 2. The high temperature
and high pressure bypassed liquid refrigerant is expanded and converted into a mixed
refrigerant (gaseous refrigerant + liquid refrigerant) with a temperature of about
20 °C. The mixed refrigerant is re-heat-exchanged via a re-heat exchanger 6a positioned
between the condenser 2 and the injection pipe 6 for heat exchange with the condenser
2 so as to be converted into a low temperature gaseous refrigerant. The low temperature
gaseous refrigerant is then injected into the intermediate compression chamber via
the injection passage 120.
[0030] As described above, in a scroll compressor 1 having the back pressure passage 110
and the injection passage 120, if an angle α formed between the back pressure passage
110 and the injection passage 120 is greater than approximately 30°, the actual pressure
within the back pressure chamber 53, as shown in FIG. 9A, may be maintained substantially
close to/at the design pressure, thereby stably supporting the orbiting scroll 50.
If the angle α therebetween is 20°, the actual pressure within the back pressure chamber,
as shown in FIG. 9B, is greater than the design pressure, which may cause the orbiting
scroll 50 to be excessively raised and pressed against the fixed scroll 40. Accordingly,
frictional loss or abrasion may occur between the orbiting scroll 50 and the fixed
scroll 40, thereby lowering the performance and/or reliability of the compressor 1.
[0031] Consequently, the angle between the injection passage 120 and the back pressure passage
110 maintains an appropriate phase difference, or angle α therebetween, so as to effectively
prevent a refrigerant injected into the intermediate compression chamber via the injection
passage from leaking into the back pressure chamber via the back pressure passage
without flowing along the proceeding direction of the compression chamber. Hence,
during a high capacity operation of the scroll compressor, a refrigerant injected
into the intermediate compression chamber via the injection passage at the middle
portion of the refrigerant cycle may be combined with a refrigerant sucked into a
suction side of the compression chamber, thereby increasing the amount of refrigerant
to be compressed, resulting in improved performance.
[0032] Similarly, if a scroll compressor as embodied and broadly described herein is applied
to a refrigerating apparatus, the efficiency of the refrigerating apparatus may also
be improved.
[0033] As shown in FIG. 10, an exemplary refrigerating apparatus 700 as embodied and broadly
described herein may include a refrigerant compression type refrigerating cycle provided
with a scroll compressor 1, a condenser 2, an expansion apparatus 3, and an evaporator
4 as shown in FIG. 8. The compressor 1 may include an injection passage through which
a portion of refrigerant flowing through the condenser 2 is injected back into an
intermediate compression chamber of the scroll compressor 1. Within the refrigerating
apparatus 700, the scroll compressor 1 may be connected to a main substrate 710, which
controls an overall operation of the refrigerating apparatus 700. A fixed scroll installed
within the scroll compressor 1 may include a back pressure passage through which refrigerant
is discharged from the intermediate compression chamber into a back pressure chamber,
and an injection passage through which refrigerant flows back into the intermediate
compression chamber via an outlet of the condenser 2. The back pressure passage and
the injection passage forms an angle therebetween of at least more than 30°, as described
above. Consequently, leakage of the refrigerant injected into the intermediate compression
chamber via the injection passage into the back pressure passage is prevented, resulting
in improved performance of the refrigerating apparatus having such a scroll compressor.
[0034] In the scroll compressor according to the present invention and a refrigerating apparatus
having the same, leakage of the refrigerant from the intermediate compression chamber
into the back pressure chamber is prevented, thereby appropriately maintaining the
pressure of the back pressure chamber, and also increasing the amount of refrigerant
within the compression chamber, resulting in improved performance of the scroll compressor
and the refrigerating apparatus in which it is installed.
[0035] A scroll compressor as embodied and broadly described herein may be applied to numerous
different types of refrigerating apparatuses, such as, for example, an air conditioning
apparatus, a refrigerating/freezing apparatus, or other refrigerating apparatus in
which compression of refrigerant is employed.
[0036] A scroll compressor as embodied and broadly described herein is capable of maintaining
an appropriate pressure inside the back pressure chamber by preventing a refrigerant,
injected from the refrigerating cycle into the intermediate pressure via the injection
passage, from being drastically leaked from the intermediate compression chamber into
the back pressure chamber, and a refrigerating apparatus having the same.
[0037] A scroll compressor as embodied and broadly described herein may include compression
chambers formed to be consecutively moved as a plurality of scrolls perform a relative
motion with being engaged with each other, a back pressure chamber formed at a bearing
surface at which the plurality of scrolls come in contact with each other and configured
to support the neighboring scrolls, a first passage formed at a fixed scroll and configured
so that part of refrigerant compressed in the compression chambers is bypassed to
be guided into the back pressure chamber, and a second passage formed at a fixed scroll
and configured so that part of refrigerant discharged from the compression chambers
into a refrigerating cycle is bypassed at a middle portion of the refrigerating cycle
to be supplied back into the compression chambers.
[0038] A scroll compressor in accordance with another embodiment as broadly described herein
may include a fixed scroll having spiral wraps, and an orbiting scroll having spiral
wraps, the spiral wraps orbiting with being engaged with the wraps of the fixed scroll
so as to form a pair of compression chambers consecutively moved during the orbiting
motion, a back pressure chamber for containing a refrigerant bypassed from the compression
chambers being formed at a rear surface of the orbiting scroll, wherein the fixed
scroll is provided with at least one back pressure passage formed at the fixed scroll
for communicating the compression chambers with the back pressure chamber, and an
injection passage through which part of a refrigerant discharged from the compression
chambers into the refrigerating cycle is injected back into the compression chambers.
[0039] A refrigerating apparatus as embodied and broadly described herein may include a
compressor, a condenser connected to a discharge side of the compression, an expansion
apparatus connected to the condenser, and an evaporator connected to the expansion
apparatus and to a suction side of the compressor, wherein the compressor is a scroll
compressor configured so that an angle between an injection passage communicating
with an intermediate compression chamber at a middle portion of a refrigerating cycle
and a back pressure passage is approximately more than 30°.
[0040] Any reference in this specification to "one embodiment," "an embodiment," "example
embodiment," etc., means that a particular feature, structure, or characteristic described
in connection with the embodiment is included in at least one embodiment of the invention.
The appearances of such phrases in various places in the specification are not necessarily
all referring to the same embodiment.
1. A scroll compressor, for compressing refrigerant, comprising:
a casing (10);
a fixed scroll (40) fixed to an interior of the casing (10);
an orbiting scroll (50) movably engaged with the fixed scroll (40) so as to form compression
chambers (P) therebetween that are consecutively moved as the orbiting scroll (50)
moves relative to the fixed scroll (40);
a back pressure chamber (S3) formed at a bearing surface formed between the fixed
(40) and orbiting (50) scrolls, wherein the back pressure chamber (S3) is configured
to support a position of the orbiting scroll (50) against the fixed scroll (40);
characterised by
a first passage (110) formed in the fixed scroll (40) and configured to guide refrigerant
compressed in the compression chambers (P) back into the back pressure chamber (S3);
and
a second passage (120) formed at the fixed scroll (40) and configured to guide refrigerant
into the compression chambers (P) from a refrigerating cycle,
an angle between the first passage (110) and the second passage (120) is greater than
approximately 30° in a circumferential direction along the wrap of the scroll, and
an outlet (112) of the second passage (120) is closer to a discharge side of the compression
chambers (P) than an outlet of the first passage (110) is.
2. The compressor of claim 1, further comprising a main frame (20) fixed to the interior
of the casing (10) so as to support the fixed scroll (40) and the orbiting scroll
(50).
3. The compressor of claim 2, wherein the back pressure chamber (S3) is defined by a
recess formed in an upper surface of the main frame (20), a lower surface of the fixed
scroll (40), and an outer peripheral portion of the orbiting scroll (50).
4. The compressor of claim 3, further comprising a groove formed in the lower surface
of the fixed scroll (40) so as to provide for communication between the first passage
(110), which is formed in the fixed scroll (40), and the back pressure chamber (S3).
5. The compressor of claim 4, wherein the first passage (110) comprises:
a first bypass hole (111) having a first end connected to the communication groove
(114);
a second bypass (112) hole having a first end alternately connected to the compression
chambers (P) as the orbiting scroll (50) moves relative to the fixed scroll (40);
and
a third bypass hole (113) that connects second ends of the first and second bypass
holes (111, 112).
6. The compressor of claim 5, further comprising a blocking member (115) positioned in
an external end of the third bypass hole (113) so as to seal the first passage (110).
7. The compressor of claim 1, wherein the second passage (120) comprises:
a first injection hole (121) that extends into a plate portion of the fixed scroll
(40); and
a second injection hole (122) having a first end connected to the first injection
hole (121) and a second end that alternately communicates with the compression chambers
(P).
8. The compressor of claim 7, wherein an inlet end of the first injection hole (121)
is connected to an injection pipe (6) that extends through an outer wall of the casing
(10) so as to receive refrigerant from an intermediate section of a refrigerating
cycle and to direct the received refrigerant back into the compression chambers (P)
through the second passage (120).
9. The compressor of claim 1, wherein the first passage (110) is formed in the fixed
scroll (40) and is configured to communicate with one of the compression chambers
(P) at an intermediate pressure between a suction pressure and a discharge pressure.
10. The compressor of claim 1, wherein the second passage (120) is formed in the fixed
scroll (40) and is configured to communicate with one of the compression chambers
(P) at an intermediate pressure between a suction pressure and a discharge pressure.
11. The compressor of claim 1, wherein a diameter of an outlet of the second passage (120)
is greater than or equal to a diameter of an outlet of the first passage (110).
1. Spiralverdichter zum Verdichten eines Kältemittels, mit:
einem Gehäuse (10);
einer feststehenden Spirale (40), die an einem Inneren des Gehäuses (10) befestigt
ist;
einer umlaufenden Spirale (50), die beweglich mit der feststehenden Spirale (40) in
Eingriff steht, um dazwischen Verdichtungskammern (P) zu bilden, die fortlaufend bewegt
werden, wenn sich die umlaufende Spirale (50) relativ zur feststehenden Spirale (40)
bewegt;
einer Gegendruckkammer (S3), die an einer Lagerfläche ausgebildet ist, die zwischen
der feststehenden (40) und umlaufenden (50) Spirale ausgebildet ist, wobei die Gegendruckkammer
(S3) konfiguriert ist, eine Position der umlaufenden Spirale (50) gegen die feststehende
Spirale (40) zu halten;
gekennzeichnet durch
einen ersten Kanal (110), der in der feststehenden Spirale (40) ausgebildet und konfiguriert
ist, in den Verdichtungskammern (P) verdichtetes Kältemittel zurück in die Gegendruckkammer
(S3) zu leiten; und
einen zweiten Kanal (120), der an der feststehenden Spirale (40) ausgebildet und konfiguriert
ist, Kältemittel aus einem Kühlzyklus in die Verdichtungskammern (P) zu leiten, wobei
ein Winkel zwischen dem ersten Kanal (110) und dem zweiten Kanal (120) in eine Umfangsrichtung
längs der Windung der Spirale größer als annähernd 30° ist, und ein Auslass (112)
des zweiten Kanals (120) einer Ausstoßseite der Verdichtungskammern (P) näher liegt
als ein Auslass des ersten Kanals (110).
2. Verdichter nach Anspruch 1, der ferner einen Hauptrahmen (20) aufweist, der am Inneren
des Gehäuses (10) befestigt ist, um die feststehende Spirale (40) und die umlaufende
Spirale (50) zu halten.
3. Verdichter nach Anspruch 2, wobei die Gegendruckkammer (S3) durch eine Aussparung
definiert wird, die in einer Oberseite des Hauptrahmens (20), einer Unterseite der
feststehenden Spirale (40) und einem Außenumfangsabschnitt der umlaufenden Spirale
(50) ausgebildet ist.
4. Verdichter nach Anspruch 3, der ferner eine Nut aufweist, die in der Unterseite der
feststehenden Spirale (40) ausgebildet ist, um eine Verbindung zwischen dem ersten
Kanal (110), der in der feststehenden Spirale (40) ausgebildet ist, und der Gegendruckkammer
(S3) bereitzustellen.
5. Verdichter nach Anspruch 4, wobei der erste Kanal (110) aufweist:
ein erstes Umgehungsloch (111), das ein erstes Ende aufweist, das mit der Verbindungsnut
(114) verbunden ist;
ein zweites Umgehungsloch (112), das ein erstes Ende aufweist, das abwechselnd mit
den Verdichtungskammern (P) verbunden ist, wenn sich die umlaufende Spirale (50) relativ
zur feststehenden Spirale (40) bewegt; und
ein drittes Umgehungsloch (113), das zweite Enden des ersten und zweiten Umgehungslochs
(111, 112) verbindet.
6. Verdichter nach Anspruch 5, der ferner ein Sperrelement (115) aufweist, das in einem
äußeren Ende des dritten Umgehungslochs (113) angeordnet ist, um den ersten Kanal
(110) abzudichten.
7. Verdichter nach Anspruch 1, wobei der zweite Kanal (120) aufweist:
ein erstes Einspritzloch (121), das sich in einen Plattenabschnitt der feststehenden
Spirale (40) erstreckt; und
ein zweites Einspritzloch (122), das ein erstes Ende, das mit dem ersten Einspritzloch
(121) verbunden ist, und ein zweites Ende aufweist, das abwechselnd mit den Verdichtungskammern
(P) verbunden ist.
8. Verdichter nach Anspruch 7, wobei ein Einlassende des ersten Einspritzlochs (121)
mit einem Einspritzrohr (6) verbunden ist, das sich durch eine Außenwand des Gehäuses
(10) erstreckt, um Kältemittel aus einem Zwischenabschnitt eines Kühlzyklus aufzunehmen
und das aufgenommene Kältemittel durch den zweiten Kanal (120) zurück in die Verdichtungskammern
(P) zu leiten.
9. Verdichter nach Anspruch 1, wobei der erste Kanal (110) in der feststehenden Spirale
(40) ausgebildet und konfiguriert ist, mit einer der Verdichtungskammern (P) mit einem
Zwischendruck zwischen einem Ansaugdruck und einem Ausstoßdruck in Verbindung zu stehen.
10. Verdichter nach Anspruch 1, wobei der zweite Kanal (120) in der feststehenden Spirale
(40) ausgebildet und konfiguriert ist, mit einer der Verdichtungskammern (P) mit einem
Zwischendruck zwischen einem Ansaugdruck und einem Ausstoßdruck in Verbindung zu stehen.
11. Verdichter nach Anspruch 1, wobei ein Durchmesser eines Auslasses des zweiten Kanals
(120) größer oder gleich einem Durchmesser eines Auslasses des ersten Kanals (110)
ist.
1. Compresseur à spirale pour la compression d'un fluide réfrigérant, comprenant:
un carter (10) ;
une volute fixe (40) montée à l'intérieur du carter (10) ;
une volute orbitale (50) en prise mobile avec la volute fixe (40) de manière à former
des chambres de compression (P) intercalées qui sont déplacées en conséquence quand
la volute orbitale (50) se déplace par rapport à la volute fixe (40) ;
une chambre de contre-pression (S3) formée sur une surface de palier entre la volute
fixe (40) et la volute orbitale (50), ladite chambre de contre-pression (S3) étant
prévue pour supporter une partie de la volute orbitale (50) contre la volute fixe
(40) ;
caractérisé par
un premier passage (110) formé dans la volute fixe (40) et prévu pour ramener le fluide
réfrigérant comprimé dans les chambres de compression (P) vers la chambre de contre-pression
(S3) ; et
un deuxième passage (120) formé sur la volute fixe (40) et prévu pour conduire le
fluide réfrigérant vers les chambres de compression (P) depuis un cycle de réfrigération,
un angle entre le premier passage (110) et le deuxième passage (120) étant supérieur
à env. 30° dans la direction circonférentielle le long de l'enveloppe de la volute,
et une sortie (112) du deuxième passage (120) étant plus proche d'un côté d'échappement
des chambres de compression (P) qu'une sortie du premier passage (110).
2. Compresseur selon la revendication 1, comprenant en outre un cadre principal (20)
monté à l'intérieur du carter (10) de manière à supporter la volute fixe (40) et la
volute orbitale (50).
3. Compresseur selon la revendication 2, où la chambre de contre-pression (S3) est définie
par une cavité formée dans une surface supérieure du cadre principal (20), une surface
inférieure de la volute fixe (40) et une partie périphérique extérieure de la volute
orbitale (50).
4. Compresseur selon la revendication 3, comprenant en outre une rainure formée dans
la surface inférieure de la volute fixe (40) pour permettre une communication entre
le premier passage (110) formé dans la volute fixe (40) et la chambre de contre-pression
(S3).
5. Compresseur selon la revendication 4, où le premier passage (110) comprend :
un premier trou de dérivation (111) avec une première extrémité reliée à la rainure
de communication (114) ;
un deuxième trou de dérivation (112) avec une première extrémité alternativement reliée
aux chambres de compression (P) quand la volute orbitale (50) se déplace par rapport
volute fixe (40) ; et
un troisième trou de dérivation (113) reliant les deuxièmes extrémités du premier
et du deuxième trou de dérivation (111, 112).
6. Compresseur selon la revendication 5, comprenant en outre un élément de blocage (115)
disposé à une extrémité externe du troisième trou de dérivation (113) de manière à
obturer le premier passage (110).
7. Compresseur selon la revendication 1, où le deuxième passage (120) comprend :
un premier trou d'injection (121) s'étendant dans une partie de plaque de la volute
fixe (40) ;
et
un deuxième trou d'injection (122) avec une première extrémité reliée au premier trou
d'injection (121) et une deuxième extrémité communiquant alternativement avec les
chambres de compression (P).
8. Compresseur selon la revendication 7, où une extrémité d'admission du premier trou
d'injection (121) est reliée à une conduite d'injection (6) traversant une paroi extérieure
du carter (10) de manière à recevoir le fluide réfrigérant d'une section intermédiaire
d'un cycle de réfrigération et pour ramener le fluide réfrigérant reçu vers les chambres
de compression (P) par le deuxième passage (120).
9. Compresseur selon la revendication 1, où le premier passage (110) est formé dans la
volute fixe (40) et est prévu pour communiquer avec une des chambres de compression
(P) à une pression intermédiaire entre une pression d'aspiration et une pression de
refoulement.
10. Compresseur selon la revendication 1, où le deuxième passage (120) est formé dans
la volute fixe (40) et est prévu pour communiquer avec une des chambres de compression
(P) à une pression intermédiaire entre une pression d'aspiration et une pression de
refoulement.
11. Compresseur selon la revendication 1, où le diamètre d'une sortie du deuxième passage
(120) est supérieur ou égal au diamètre d'une sortie du premier passage (110).