CN105705899A

CN105705899A - Heat pump for a household appliance

Info

Publication number: CN105705899A
Application number: CN201480060807.2A
Authority: CN
Inventors: F·巴尔塞洛鲁埃斯卡斯; J·贡萨尔维斯马西亚; I·奥特洛加西亚; R·圣马丁桑乔
Original assignee: BSH Bosch und Siemens Hausgeraete GmbH
Current assignee: BSH Hausgeraete GmbH
Priority date: 2013-11-06
Filing date: 2014-11-03
Publication date: 2016-06-22
Also published as: WO2015068092A1; PL3066406T3; ES2659046T3; EP3066406A1; EP3066406B1

Abstract

The heat pump P is designed for a household appliance H, in particular laundry treatment appliance H, and comprises a rotary compressor 1, a condenser 2, a restrictor 3, and an evaporator 4, wherein the condenser 2 is of an expanded tube-and-fin type with the tubes 11 having an outer diameter dc of less than 7 mm and wherein the roller (16) has a height-to-radius ratio of 1.4 to 1.2. A household appliance H, in particular a laundry treatment appliance H, comprises such heat pump P.

Description

Heat pump for home appliances

Technical field

The present invention relates to a kind of heat pump for home appliances, especially laundry treatment appliance, this heat pump includes compressor, condenser, reducer and vaporizer。The invention still further relates to and a kind of include the home appliances of this heat pump, especially laundry treatment appliance。

Background technology

This clothesdrier with heat pump generally includes refrigerant loop and air path。Described refrigerant loop includes the compressor, condenser, reducer and the vaporizer that are connected in series by refrigerant line。Cold-producing medium flows through compressor, condenser, reducer and vaporizer (with this order), and by by they interconnective pipelines。Cold-producing medium when process air flows through air path by means of condenser by heat release to process air, and obtain heat and dampness by means of vaporizer from flow through the process air of air path。Compressor converts mechanical energy into heat energy by compressing the cold-producing medium in refrigerant loop。

In air path or process air loop, process air flow to vaporizer from cylinder。At drum outlet place, air is in moderate temperature and relatively wet。At vaporizer place, air is cooled and dehumidifies and flows to condenser subsequently, and air is heated at condenser place。Heat and dry air and then be introduced in cylinder, the medicated clothing held from cylinder at cylinder air absorbs dampness。Thus, vaporizer and condenser act on as the heat exchanger with refrigerant side and process air side。As shown in prior art document EP1632736A2, EP1593770B1, WO2013/060626A1, WO2013/023958A1, WO2012/065916A1, WO2011/080045A1, US2010/0154248A1 and US2011/0209484A1, heat pump use in clothesdrier and its normal arrangement are generally known in the art。

Vaporizer and condenser can be fin-tube types。The pipe of vaporizer and condenser can be the entity separately as shown in prior art document WO2008/004802A3, EP2261416A1, EP2244044A2, EP2644768A1, EP2418448A1, WO2013/153972A1, EP2468948A2 and EP1593770B1, or can be connected in as shown in prior art document WO2008/004802A3 in common core。In being parallel to the front view of length of described pipe, described Guan Kecheng column (or row) is arranged, described column (or row) respectively includes multiple pipe。Distance between adjacent column is referred to as " longitudinal pitch ", and the distance between the adjacent tubes of string is referred to as " horizontal spacing "。

Vaporizer and another typical construction of condenser are so-called aluminum single hoses (frost-free type), and wherein, aluminum pipe is bent and fin is arranged along aluminum pipe when being absent from pipe expansion (expansion)。

The vaporizer used in heat pump drier at present and the overall diameter of the pipe of condenser are as follows: be 3/8 for Fin and tube evaporator and condenser " (9.525mm) and 7mm, and be 8mm for aluminum single hose vaporizer and condenser。

There is the efficiency (in kWh/kg) of raising including the clothesdrier of heat pump compared with the traditional clothesdrier only using electric heater。Therefore, compared with conventional dryer, the CO2 emission relevant with operation including the clothesdrier of heat pump is generally lower due to its relatively low power consumption。But, the cold-producing medium and its GWP (" global warming potential ") that use in heat pump must be considered, and GWP promotes total TEWI (" warm and affect total yield ") by cold-producing medium to the direct or indirect discharge in air。Nowadays, the typical cold-producing medium used in heat pump is that fluorinated hydrocarbon compounds (HFC), the GWP of fluorinated hydrocarbon compounds may be up to 1500 or even higher。

The probability reducing the TEWI of these systems is the hydrocarbon refrigerant using and having low GWP, such as R-290 (propane) or R-1270 (propylene)。These cold-producing mediums major downside is that they are inflammable, therefore the maximum charge of cold-producing medium in clothesdrier is limited to 150g by IEC60335-2-11 standard。It is generally known that can have a best refrigerant charge amount for particular system, but the fixed 150g cold-producing medium restriction of IEC60335-2-11 standard is usually less than the best charge of the cold-producing medium for clothesdrier heat pump。

Efficiency is machine impact by compression also。Such as, the efficiency of rotary compressor is affected by the different geometrical size of its parts, including the physical dimension of floss hole, suction inlet, rotor and cylinder。The change of these physical dimensions means the difference of the thermokinetics behavior of cold-producing medium in the difference of mechanical friction and compressor。In more detail, in compressor, determine that the loss of compressor efficiency includes following loss: come from the energy loss of the loss of electric machine, frictional dissipation, the compression loss produced because of undesirable compression, the valve loss produced because of air pulsing and overcompression and lubricant pumping loss and come from the mass flow loss of the clearance volume loss produced because of valve and cylinder head size, leakage loss, backflow loss, the suction gas that produces because of the gas density of cylinder porch add thermal losses and the loss produced because of lubricant stream。

Summary of the invention

It is an object of the invention to overcome the of the prior art at least some problem relevant to the heat pump for home appliances, especially laundry treatment appliance at least in part, and especially providing a kind of heat pump for home appliances, especially laundry treatment appliance, described heat pump has the GWP of reduction and the efficiency of raising。

This purpose is realized by the feature of independent claims。Preferred embodiment is especially in the dependent claims, be suggested in the following description and in the accompanying drawings。

Therefore, this purpose is by realizing for the heat pump of home appliances, especially laundry treatment appliance, described heat pump includes compressor, condenser, reducer and vaporizer, they are connected in series by accommodating the refrigerant loop of flammable coolant, wherein, described condenser (" condenser coil ") is fin-tube type, and it has the overall diameter pipe less than 7mm。

This causes the bigger heat transmission from refrigerant side to air side, its mode is, reduce the system volume for cold-producing medium, increase refrigerant side place convection coefficient, pressure loss and air side secondary surfaces (secondarysurface) even if size between set up good balance, permission cold-producing medium cooling (that is, higher supercool (subcooling)) in low charge situation and reach suitable condensing pressure。This can be even 150 grams by the flammable coolant amount in described heat pump or less realize。

Described laundry treatment appliance especially can be clothesdrier。Described home appliances can also be washing machine, dish-washing machine, cooling device etc.。

The refrigerant/air heat exchanger that condenser and vaporizer are typically arranged to heat exchanger, are especially passed through by the process air of described home appliances。

In a preferred variant or embodiment, for fin-tube type, it has the pipe of 7mm or less overall diameter to described vaporizer (" evaporator coil ")。

In another preferred variant, the overall diameter of the pipe of described condenser (" condenser coil ") be about 6mm or less, especially for 5.5mm or less, especially for 5mm or less。

In another preferred embodiment, the horizontal spacing of the pipe of condenser is 21mm or less, and longitudinal pitch is 19mm or less。This causes the bigger heat transmission from refrigerant side to air side, its mode is, even if increasing the convection coefficient at air side place, setting up good balance between the size of pressure loss and the secondary surfaces of air side, permission cold-producing medium cooling in low charge situation (that is, higher supercool) and reach suitable condensing pressure。It may be preferred that: this is also applied for the pipe of evaporator coil and evaporator coil。

In order to improve the efficiency of compressor, especially rotary compressor, it is preferred that the height radius ratio of the rolled portion of compressor is 1.4 to 1.2, is especially less than 1.4。Rolled portion especially can be formed to have the hollow cylinder of the height measured along its longitudinal axis。Radius is generally from longitudinal axis to the overall diameter vertical survey of described cylinder。This embodiment reduces frictional dissipation, and realize identical cooling capacity to improve the efficiency of compressor from there through with low input power。For the height radius ratio of described rolled portion of rotary compressor of clothesdrier between 1.7 to 1.5。In the special modified example of the compressor according to the present invention, described height radius ratio is between 1.4 to 1.2。

In another preferred embodiment, the area of the floss hole of compressor, especially rotary compressor is 19.8mm²(square millimeter) or bigger。This point and the pressure passing through to reduce in dump valve decline, and also achieve the raising (the identical cooling capacity in relatively low input power situation) of described compressor efficiency。

In another preferred embodiment: the discharge capacity of compressor is between 6cc (cubic centimetre) to 9.5cc。If compressor displacement is more than 9.5cc, then the heating efficiency being likely to need to improve condenser place is so as to make the energy from compressor pump suitably dissipate。This will imply that bigger condenser area and volume。This will and then need to increase refrigerant charge amount to allow cold-producing medium to condense within the condenser, owing to drying machine safety criterion is for the restriction of flammable coolant 150g, increases refrigerant charge amount and is not expected to。If described compressor displacement is lower than 6cc, then mass flow of refrigerant will decline so many so that the energy transmission in heat exchanger is affected negatively。

In another preferred embodiment: the oil mass in compressor between 150cc to 210cc for improve performance。In particular it is preferred that the oil mass equal to or less than 180cc。

Preferably: the dissolubility in the refrigerant of the oil in compressor reduces。Especially, dissolubility is lower than 35%。This is especially suitable in the following operating point situation of heat pump drier, i.e. the mixing temperature that the condensing pressure situation downforce at 70 DEG C is about 26bar (such as 26+/-0.5bar) and oil and such as R290 is 80 DEG C。Spendable refrigerant amount in the appropriately combined raising heat exchanger of oil type and oil mass, and guarantee that at compressor place good lubrication and internal leakage seal to provide good volume efficiency。This embodiment makes use of the fact that the primary amount of the cold-producing medium of heat pump is arranged in condenser coil (the relatively high density due to the high internal volume of condenser coil and cold-producing medium) and compressor (cold-producing medium mixes with oil within the compressor)。The cold-producing medium mixed with oil in compressor can not be used for energy transmission purpose in a heat exchanger。Therefore, the amount of the cold-producing medium mixed with oil in compressor is more big, in a heat exchanger for reaching the amount more little (especially under the system according to drying machine standard IEC 60335-2-11,150g flammable coolant restriction) of the spendable cold-producing medium of best operating point。In other words, the amount of the cold-producing medium mixed with oil in compressor is more little, and the amount of the cold-producing medium in heat exchanger is more big。This so cause following impact: supercool being enhanced remains overheated constant, dehumidifying rate increases (the high enthalpy difference due in vaporizer), and, the reduction of compressor power consumption is anticipated owing to low frictional dissipation and consequent compressor efficiency improve (that is, identical when compared with low input power cooling capacity)。This means, for instance as common result, drying time and the energy expenditure of arid cycle are reduced。

In order to also realize or in order to support the above-mentioned advantage of the present embodiment, i.e. the oil mass in compressor is between 150cc to 210cc, and described oil preferably has kinematic viscosity。1.5mm²/ s (cSt) to 4mm²Mixture viscosity between/s is preferred, especially at heat pump drier operating point place。Heat pump drier operating point such as can have the mixing temperature of the pressure (having the condensing pressure being at 70 DEG C) more than 26bar and oil and 80 DEG C of R290。The range of viscosities preferably with oil phase previously used ratio with greater value seals (due to the low-density of R290, this point is especially preferred) with the good internal leakage guaranteeing in compressor and thus improves compressor volume efficiency。The high level of these kinematic viscositys causes high frictional dissipation (negative effect to compressor efficiency)。Overall situation is: when use there is high kinematic viscosity oily time, compressor efficiency improves。

For using preferably within the compressor: polymer poly aklylene glycol (PolyalkyleneGlycols) (" PAG ") and polyhydric alcohol ester oil (PolyolesterOils) (" POE ")。Oily kind or their equivalent of following compressor are especially preferred: (i) PAGPZ100S (from IdemitsuKosan company limited), it has 3.8mm²The mixing viscosity of/s and 30% dissolubility and (ii) POERB-P68EP (from JXNipponOil&Energy company), it has 1.6mm²The mixing viscosity of/s and 24% dissolubility。These values are with reference to the running parameter being in its operating point place, the i.e. about pressure (having the condensing pressure in 70 DEG C of situations and the mixing temperature with such as 80 DEG C of R290) of 26bar of heat pump driers。These oil have an advantage that they show that the beneficial value of oil kinematic viscosity, described oil kinematic viscosity are preferred to guarantee that good internal leakage seals, in order to improve compressor volume efficiency and therefore improve compressor efficiency。These oil have following extra advantage: with other in heat pump drier compressor compared with the oil of normally used same type, POERB-68EP such as, they have relatively low dissolubility in the refrigerant。

Table 1 illustrate under these conditions from R290 mixing different oil between contrast。

Although, in another preferred embodiment, the cold-producing medium of the vapor compression system of heat pump is inflammable cold-producing medium, especially R290 (propane)。But, other any applicable flammable coolant, such as R-1270 (propylene) can be used。

In another preferred embodiment, using propane (R290) as cold-producing medium and in conjunction with fin-tube type condenser coil, it has the pipe of 5mm overall diameter。Described evaporator coil is also fin-tube type, and it has the pipe of 7mm overall diameter。Rotary compressor has less than 9.5cc and the discharge capacity higher than 6cc。Described compressor includes the rolled portion of the height radius ratio having between 1.40 to 1.20。The area of the floss hole of described compressor is more than 19.8mm²。Oil mass in compressor is between 150cc to 210cc。Following modified example is especially preferred: the type of oil is the PAGPZ100S (or equivalent) from IdemitsuKosan company limited；The type of oil is the POERB-P68EP (or equivalent) from JXNipponOil&Energy company。The horizontal spacing of the pipe of described condenser coil is less than 21mm, and longitudinal pitch is less than 19mm。In particular it is preferred that: the horizontal spacing of the pipe of described condenser coil is about 19mm (such as: 19.05mm), and longitudinal pitch is about 16.5mm。

By using the condenser coil of pipe with 5mm overall diameter, it is achieved that in condenser coil, the situation of interior volume specific ratio 7mm pipe shared by cold-producing medium is low by 12%。Internal volume is more little, more few for the refrigerant amount needed for filling condenser coil。The less overall diameter of 5mm be also translated into drying machine performance improvement, namely reduce 13% drying time and reduce by 11% energy expenditure。When use there is the condenser of 7mm pipe, for realizing the similar drying machine performance energy expenditure of high 4% (that is, the identical drying time and), it is necessary to the R290 of 210g。In this case, IEC60335-2-11 standard will be violated。

This purpose of the present invention realizes also by the home appliances including heat pump as above。Laundry treatment appliance especially can be clothesdrier, such as independent equipment or as washing/drying combination unit。Described home appliances can also be washing machine, dish-washing machine, cooling device etc.。

Generally, the invention allows to use steam compressor arrangement or heat pump laundry dryer, it has Hydrocarbon or other any flammable fluid as cold-producing medium, and described cold-producing medium has low charge and high efficiency。Traditional solution uses the high volume (known solution uses to be had higher than 190g refrigerant charge amount, 9.52mm, 8mm or 7mm overall diameter heat exchanger) in refrigerant loop, and using high oil mass, described oil has high dissolution rate in the refrigerant。Due to IEC60335-2-11 fixed, for the restriction of flammable coolant 150g, traditional solution can not have enough supercool。This is that described condenser coil is the part in cooling circuit owing to lacking cold-producing medium in condenser coil, and described cooling circuit has the highest internal volume and thus the highest refrigerant amount。When use has the condenser coil less than 7mm (i.e. 5mm) overall diameter, the internal volume of condenser is reduced, so that for the cold-producing medium of equal in quality, it is possible in condenser coil, obtain bigger refrigerant density。Obtain the high liquid ratio of the liquid phase of cold-producing medium therewith, this so that cause the condensation earlier of cold-producing medium in condenser。Hereby it is achieved that be conducive to the higher supercool of cooling capacity。Additionally, that use relatively low amount and that the miscibility of cold-producing medium is relatively low oil so that the cold-producing medium of relatively low amount mixes with oily in compressor。Thus, the cold-producing medium of higher amount can be used for heat transmission purpose in a heat exchanger。Additionally, the appropriately designed of compressor physical dimension (that is, rolled portion size and floss hole area) improves compressor efficiency by reduction frictional dissipation and raising volume efficiency。

For clothesdrier, this causes that energy expenditure reduces (in the scope of such as 12% to 17%, especially 14.5%), and this produces relatively low TEWI (warm and affect total yield) value。Additionally, drying time reduces about 20.8%。

Accompanying drawing explanation

In the accompanying drawings, schematically show the present invention by exemplary embodiment and the present invention will be illustrated by further referring next to this exemplary embodiment。Accompanying drawing illustrates:

Fig. 1 illustrates the schematic diagram of the home tumble drying machine using heat pump；

Fig. 2 illustrates the cutaway top view of condenser；

Fig. 3 A illustrates the front view of the condenser of Fig. 2；

Fig. 3 B illustrates the front view of the bend pipe of the condenser of Fig. 3 A；

Fig. 3 C illustrates the front view of the bending section of the condenser of Fig. 3 A；

Fig. 4 illustrates the top view of the rotary compressor opened；And

Fig. 5 illustrates the sectional side view of the rotary compressor opened of Fig. 4。

Detailed description of the invention

Fig. 1 illustrates the laundry treatment appliance in home tumble drying machine H-shaped formula。Cylindrical drier H includes heat pump P, and described heat pump at least has compressor 1, fin-tube type condenser 2, reducer 3 and Fin and tube evaporator 4 as element。Element 1-4 is connected in series by refrigerant tubing 5 in the order shown, to form refrigerant loop or path。

Cylindrical drier H also includes process air loop or path 6, and process air A flows in described air loop or path。Air loop 6 includes the rotatable drum 7 for holding pending medicated clothing。Air A leaves cylinder 7 with moderate temperature and humidity。Then, air A flows to vaporizer 4, and described vaporizer is positioned at cylinder 7 downstream in air loop A and works as heat exchanger。At vaporizer 4 place, air A is cooled and condenses。Produced condensate is collected in water tank W。At vaporizer 4 place, the cold-producing medium R that air A also cools down and is delivered on vaporizer 4 by a part for its heat energy and thus passes in vaporizer 4。This makes vaporizer 4 from liquid condition, cold-producing medium R can be changed into gaseous state。

Further downstream at air loop 6, the air A of now dry and cooling is by condenser 2, at described condenser place, causes adding hot-air A to the heat transmission of air A respectively from condenser 2 and cold-producing medium R and cold-producing medium R is cooled to its liquid condition。Now warm and dehumidified/dry air A is introduced again in cylinder 7 subsequently, in order to heats laundry also absorbs dampness。Cold-producing medium R moves in refrigerant loop 1-5 by compressor 1。Cold-producing medium R is inflammable cold-producing medium, especially R290。The total amount of inflammable cold-producing medium R is 150g or less。

Thus, vaporizer 4 and condenser 2 use as heat exchanger。

This cylindrical drier H and heat pump P thereof (includes refrigerant loop 1-5) and the operation of its air loop 6 is it is well known that from without being explained in more detail。

Fig. 2 illustrates the cutaway top view of (expanded) fin-tube type condenser 2 of expansion。Condenser 2 includes 5 essentially identical U-shaped bend pipes 8, and described bend pipe has identical orientation and arranges in same direction。Although for the sake of simplicity, bend pipe 8 illustrates in the same plane, but they are usually placed in three dimensional structure。Bend pipe 8 is mechanically connected and is thermally coupled to the attachment structure formed by a folded fin 9。This folded fin 9 F and rear side B on front side of it is covered for mechanical protection by corresponding end plate 10。The straight flange 11 of bend pipe 8 is in vertical manner through fin 9。Thus, the bending section of bend pipe 8 or bending section 12 are all located at the side of this folded fin 9, and (opening) end 13 of bend pipe 8 is all located at the opposite side of this folded fin 9。This folded fin 9 provides rigidity for condenser 2, and limits the relative motion of bend pipe 8。Thus, this folded fin 9 limits or weakens the power being externally introduced and the element being transferred to condenser 2 that moves。

Bend pipe 8 connects to form open end formula fluid passage。For this purpose it is proposed, connected in couples by bend pipe 8 so that middle bend pipe 8 is connected to corresponding bend pipe 8 on two ends 13, and (or being positioned at end) bend pipe 8 of two ends is respectively connected to middle bend pipe 8 on only one end 13。The other end 13 of each end bend pipe 8 is not attached to bend pipe 8, and is coupled to corresponding refrigerant line 5。

The pipe using the pipe bend 14 in the bending 180 ° channel bend 14 of C type (U-shaped or) form realizes the connection between bend pipe 8。Pipe bend 14 is such as attached to the open end of bend pipe 8 by solder brazing (brazing) or solder (soldering), especially torch brazing or torch soldering, durable especially, closely and have cost-efficient connection to realize。

Bend pipe 8 and/or pipe bend 14 can by identical materials, such as aluminum or copper one-tenth。Alternatively, as it can be seen, bend pipe 8 and/or pipe bend 14 can be made by different materials, such as aluminum (not shown in phantom) and copper (shown in phantom)。The overall diameter of bend pipe 8 and/or pipe bend 14 is 7mm or less, actually have ignored the end sections being likely to expand, and bend pipe 8 and pipe bend 14 bond together at described end sections。At this, the overall diameter dc of bend pipe 8 and/or pipe bend 14 is 5mm。

Thus, the fin-tube type condenser coil 8,14 of meander shape is defined。By refrigerant line 5, inflammable cold-producing medium R, such as R290 can be introduced into condenser coil as shown in straight arrow and neutralize from condenser coil 8,14 discharge。

Fig. 3 A illustrate the condenser of Fig. 2, along Fig. 2 to the front view of the direction F on condenser 2, here it is shown that 8 rather than 5 bend pipes 8。As shown in Figure 3 B, it is shown that overall diameter dc is U-shaped or C type pipe bend 14 5mm, prominent forward, and as shown in Figure 3 C, it is shown that have its rearwardly projecting bending section 12, overall diameter dc be the bend pipe 8 of 5mm。Bend pipe 8 and/or pipe bend 14 can be made by different materials, such as aluminum (not shown in phantom) and copper (shown in phantom) again。Condenser 2 has three dimensional structure, it is shown that three dimensional structure is for good heat exchange and is used for being readily disposed in cylindrical drier H。

The straight flange 11 of bend pipe 8 is arranged with parallel row C。Adjacent row C has fore-and-aft distance or the spacing dL of 19mm or less。Lateral separation or spacing dT between the adjacent straight flange 11 of identical row C are 21mm or less。Especially, horizontal spacing dT is 19.05mm and longitudinal pitch dL is 16.5mm。

As shown in Fig. 2 and Fig. 3 A to 3C, identical basic structure also apply be applicable to vaporizer 4。But, the bend pipe 8 of evaporator coil and/or pipe bend 14 preferably can have overall diameter bigger compared with the overall diameter of condenser coil 8,14, such as 7mm。

Fig. 4 illustrates the top view of the rotation compressor 1 of home tumble drying machine H。Fig. 5 illustrates the sectional side view of the rotation compressor 1 of Fig. 4。

Compressor 1 includes the outside cylinder 15 with chamber 15a, and described chamber housing has cylindrical rolled portion 16。Rolled portion 16 is supported by the end face 17 of outside cylinder 15。Rolled portion 16 can move along end face 17 or slide。The longitudinal axes L 1 of outside cylinder 15 and the longitudinal axes L 2 of rolled portion 16 are arranged in parallel but the spacing that is spaced。Rolled portion 16 is rollably rotated in outside cylinder 15 by axle 18, and described axle 18 is connected to motor (not shown)。Axle 18 is coaxial with outside cylinder 15 and thus not coaxial with rolled portion 16。In order to make rolled portion 16 rotate in outside cylinder 15, axle 18 has the cam 19 (only figure 5 illustrates) of lateral register, and rolled portion 16 is depressed on the medial wall 20 of outside cylinder 15 by described cam。Thus, rolled portion 16 and medial wall 20 have contact point K。When axle 18 rotates, this axle makes rolled portion 16 roll along sidewall 20。Now, contact point K draws the ring of Guan Bi in the path at medial wall 20 place。The discharge capacity for a complete rotation of compressor 1 is between 6cc to 9.5cc。

Axle 18 is formed as hollow cylinder, so that axle is connectable to oil pump (not shown), in order to by oil supply to compressor 1。Oil mass in compressor 1 is between 150cc to 210cc, is preferably 180cc or less。This oil especially can be RB-P68EP or the equivalent of PAGPZ100S or 68cSt of 100cSt。

Blade 21 projects in the chamber 15a of outside cylinder 15。Outside cylinder 15 also has suction inlet 22 and floss hole 23, and the wall of described suction inlet traverse outside cylinder is with by the 15a of refrigerant suction room, and described floss hole 23 traverse end face 17 is to discharge cold-producing medium。The area Q of floss hole 23 is 19.8mm²Or bigger, be preferably greater than 19.8mm², be preferably 20mm²Or bigger, be preferably 21mm²Or it is bigger。

In order to operate described compressor, cover cap (not shown) is placed on the open sides of outside cylinder 15。Cover cap can have the axle sleeve for axle 18。

In Figure 5, height h is relative to being between 1.4 to 1.2 than (height radius than) shown in the radius r to rolled portion 16 outer surface, it is preferred to less than 1.4。

Certainly, the invention is not restricted to shown embodiment。

Reference numerals list

1 compressor

2 condensers

3 reducers

4 vaporizers

5 refrigerant lines

6 process air loops/path

7 rotatable drums

8 bend pipes

9 fins

10 end plates

The straight flange of 11 bend pipes

The bending section of 12 bend pipes or bending section

The end of 13 bend pipes

14 pipe bends

15 outside cylinder

The chamber of 15a outside cylinder

16 rolled portion

The end face of 17 outside cylinder

18 axles

19 cams

The medial wall of 20 outside cylinder

21 blades

22 suction inlets

23 floss holes

A process air

On rear side of B

C pipe arranges

DL fore-and-aft distance or spacing

DT lateral separation or spacing

On front side of F

H height

H cylindrical drier

K contact point

The longitudinal axis of L1 outside cylinder

The longitudinal axis of L2 rolled portion

P heat pump

Q floss hole area

The radius of r rolled portion

R cold-producing medium

W water tank

Claims

1. a heat pump (P), it is used for home appliances (H), described heat pump includes having the rotary compressor (1) of rolled portion (16), condenser (2), reducer (3) and vaporizer (4), wherein, described condenser (2) is the fin-tube type launched, it has the overall diameter (dc) pipe (11) less than 7mm, and wherein, described rolled portion (16) has the height radius ratio of 1.4 to 1.2。

2. a heat pump as claimed in claim 1 (P), it is characterized in that, the horizontal spacing (dT) of the pipe (11) of described condenser (2) is 21mm or less, and longitudinal pitch (dL) is 19mm or less。

3. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that the area (Q) of floss hole (23) is 19.8mm²Or it is bigger。

4. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that the discharge capacity of described compressor (1) is between 6cc to 9.5cc。

5. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that the oil mass in described compressor (1) is between 150cc to 210cc。

6. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that the oil type in described compressor (1) is equal to: PAGPZ100S and/or POERB-P68EP。

7. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that the oil in described compressor has the dissolubility less than 35% in the refrigerant。

8. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that the cold-producing medium of described heat pump (P) is flammable coolant, especially R290。

9. such as heat pump in any one of the preceding claims wherein (P), it is characterised in that

-described condenser (2) is the fin-tube type launched, and it has the pipe (11) that overall diameter (dc) is 5mm,

The horizontal spacing (dT) of the pipe (11) of-described condenser (2) less than 21mm and longitudinal pitch (dL) less than 19mm,

-evaporator coil is the fin-tube type launched, and it has the pipe that overall diameter is 7mm,

-described compressor (1) has less than 9.5cc the discharge capacity higher than 6cc,

-described compressor (1) includes rolled portion (16), and described rolled portion has the height radius ratio between 1.40 to 1.20,

The area (Q) of the floss hole (23) of-described compressor (1) is more than 19.8mm²,

Oil mass in-described compressor (1) is between 150cc to 210cc。

10. heat pump (P) as claimed in claim 10, it is characterised in that the horizontal spacing (dT) of the pipe (11) of described condenser (2) is about 16.5mm for about 19mm and longitudinal pitch (dL)。

11. a home appliances (H), described home appliances includes such as heat pump in any one of the preceding claims wherein (P)。

12. home appliances (H) as claimed in claim 11, described home appliances is embodied as laundry treatment appliance。