High speed egg breaking apparatus

A multiplicity of shell eggs to be broken are first transported in transverse rows on an infeed conveyor, from which they are loaded onto a transfer conveyor. This transfer conveyor extends at a right angle to the infeed conveyor, so that the successive transverse rows of shell eggs on the infeed conveyor are rearranged into a longitudinal row on the transfer conveyor. The shell eggs are subsequently transferred from the transfer conveyor onto respective egg breaker assemblies mounted at longitudinal spacings on an endless breaker conveyor, while the breaker assemblies are traveling side by side with the transfer conveyor. The breaker assemblies break the shell eggs, and the white and yolk recovered therefrom are separated by recovery cup assemblies also carried by the breaker conveyor under the respective breaker assemblies. As an incidental feature, an air nozzle assembly is mounted on the breaker conveyor in the vicinity of each breaker assembly. Supplied with pressurized air from an air supply mechanism on one of the rotary wheels around which the breaker conveyor extends, each air nozzle assembly applies forced streams of air into a broken eggshell on one of the breaker assemblies for the recovery of the residual liquid therefrom.

BACKGROUND OF THE INVENTION 
This invention relates to egg processing in general and, in particular, to 
a method of, and apparatus for, breaking shell eggs at a high rate on an 
industrial scale. 
Industrially, most eggs to be converted to egg products are broken by high 
speed mechanical breakers. These machines separate the yolk and albumen, 
the latter being more commonly known as the white. As heretofore 
constructed, the egg breakers have had several drawbacks limiting their 
production rates. 
One of the drawbacks arises in connection with the feeding of shell eggs 
into the breaker. A typical conventional feeding scheme has been such that 
shell eggs to be broken are first washed on an infeed conveyor, from which 
they are loaded directly on respective egg breaker assemblies mounted at 
longitudinal spacings on a looped conveyor of the breaker. A difficulty 
has been encountered in thus loading the eggs on the breaker assemblies in 
the correct attitude. Unless loaded correctly, the eggs cannot be cut and 
severed in the middle portion of each egg by the breaker assemblies, 
making difficult the thorough recovery of the white and yolk therefrom. 
The higher the rate is made at which eggs are loaded on the breaker 
assemblies from the infeed conveyor, the more improperly are they 
positioned on the breaker assemblies. Thus the conventional feeding 
practice has been a bottleneck in the high speed processing of eggs. 
Another problem is the incomplete recovery of egg contents. Generally, in 
egg breakers of the type under consideration, shell eggs are held 
recumbently by the respective breaker assemblies. Each breaker assembly 
has a pair of knives movable toward and away from each other. Held against 
each other, the pair of breaker knives cut into a shell egg at its 
midpoint from below and then move apart to separate the shell into two 
pieces, thereby causing the white and yolk to drop into a recovery cup 
assembly. All the shell eggs are not necessarily broken in the intended 
manner, however, as some of them may be held by the breaker assemblies in 
other than the correct recumbent attitude. Part of the white or even the 
yolk may remain in the broken shells. Such residues have heretofore been 
discarded with the shells. 
An obvious solution to this problem is to apply forced streams of air into 
the broken eggshells while they are still being carried by the breaker 
assemblies. The residual liquid will be blown out of the shells for 
recovery in the underlying recovery cup assemblies. This solution is not 
so easy to practice as it may seem, however, for the following reasons. 
The egg breaker assemblies are mounted as aforesaid on the looped breaker 
conveyor. While traveling at constant speed along the looped path, the 
breaker assemblies receive shell eggs from the infeed conveyor, break 
them, and have their shells unloaded. The recovery of the residual liquid 
from the broken shells must be performed on the traveling breaker 
assemblies at some stage between the breaking of the shell eggs and the 
unloading of the broken shells. It is uneconomical, or rather totally 
impractical, to mount sources of pressurized air on the breaker conveyor 
for the respective breaker assemblies. Perhaps the only practical scheme 
is to provide air nozzles on the breaker conveyor for the respective 
breaker assemblies and to supply pressurized air to the nozzles while the 
breaker assemblies are traveling through a predetermined region along the 
breaker conveyor path. A difficulty arises, however, in such controlled 
supply of pressurized air to the traveling nozzles from a fixed source. A 
rotary valve would do if the nozzles revolved about a single axis. The 
breaker conveyor turns around several sprockets or like wheels and so 
inhibits the use of a simple rotary valve. No satisfactory alternative has 
so far been suggested, so that the pneumatic recovery of the residues from 
broken eggshells has just been a paper plan. 
The known high speed egg breakers have also had difficulties with regard to 
the recovery cup assemblies designed to separate the white and yolk. Each 
recovery cup assembly comprises a yolk cup just under one of the egg 
breaker assemblies on the breaker conveyor, and an albumen cup underlying 
the yolk cup. The yolk cup receives both white and yolk from the broken 
egg and allows the white to flow out of a recess cut in its side wall. 
In the yolk cup of prior art design, the recess has not been well adapted 
for the complete outflow of the white, often allowing part of the white, 
particularly the dense albumen, to remain in the yolk cup along with the 
yolk. It is also a disadvantage that the recess has been so positioned on 
the yolk cup that the recovered yolk is discharged therefrom through the 
recess. The yolk on flowing through the recess has been easy to have its 
enclosing membrane broken and thus to smear the cup, necessitating its 
cleaning. Of course the yolk cup remains unsmeared if the yolk is 
discharged intact. 
Furthermore, the conveyor for transferring the eggs in the conventional 
apparatus has a plurality of pairs of convex rolls parallel to each other 
on which each egg is supported and transferred to the successive process. 
However, in such a pair of convex rolls, if the eggs are extremely large, 
they cannot be supported stably on the rolls and sometimes they fall down 
from the rolls because the size of the rolls is fixed or unchangeable. 
SUMMARY OF THE INVENTION 
Generally, the invention has been made with a view to drastically 
increasing the production rates of egg breakers of the type defined. More 
specifically, for the attainment of this general objective, the invention 
seeks to make possible the feeding of shell eggs into the machine at a far 
higher rate than hitherto. Further, the invention aims at the complete 
recovery of the liquid contents of eggs, particularly by realizing the 
pneumatic, forced removal of the residual liquid from within the broken 
eggshells. The invention also seeks to efficiently and thoroughly separate 
the recovered white and yolk without rupturing the enveloping membrane of 
the latter. 
According to one aspect of the invention there is provided a high speed egg 
breaking method such that a multiplicity of shell eggs to be broken are 
transported in transverse rows on an infeed conveyor. Each transverse row 
of shell eggs are transferred at one time from the infeed conveyor onto a 
transfer conveyor laid at a right angle therewith. Thus the successive 
transverse rows of shell eggs on the infeed conveyor are rearranged into a 
longitudinal row on the transfer conveyor. This single row of shell eggs 
on the transfer conveyor are again transferred therefrom onto respective 
egg breaker assemblies being carried by a breaker conveyor while the 
latter is running side by side with the transfer conveyor. Then the shell 
eggs are broken by the breaker assemblies for the recovery of the white 
and yolk therefrom, and the broken shells are subsequently removed from 
the breaker assemblies. 
The invention also provides, according to another aspect thereof, apparatus 
comprising the above recited infeed conveyor, transfer conveyor, and 
breaker conveyor with the egg breaker assemblies thereon. Also, included 
are recovery cup assemblies carried by the breaker conveyor just under the 
respective egg breaker assemblies for receiving the white and yolk from 
the broken eggs. 
Preferably the transfer conveyor has pairs of concave rolls mounted thereon 
at longitudinal spacings equal to the spacings between the egg breaker 
assemblies on the breaker conveyor. Receiving shell eggs from the infeed 
conveyor, the pairs of concave rolls are adapted to rearrange them into 
the correct recumbent attitude preparatory to unloading them onto the egg 
breaker assemblies. This transfer of the shell eggs from concave roll 
pairs to breaker assemblies is carried out while the transfer conveyor and 
the breaker conveyor are traveling in the same direction at the same 
speed. Consequently the shell eggs can be placed on the breaker assemblies 
with their recumbent attitude unchanged. The correct mounting of the eggs 
on the breaker assemblies is a requirement for the proper breaking thereof 
by the breaker assemblies. Thus the method and apparatus of this invention 
are well adapted for the high speed processing of eggs. 
The method and apparatus of the invention may comprise an additional step 
of or means for, pneumatically recovering the residual liquid from within 
the broken eggshells being carried by the breaker assemblies on the 
breaker conveyor. The pneumatic residue recovery means comprise air nozzle 
assemblies operatively mounted on the breaker conveyor in the vicinities 
of the respective egg breaker assemblies thereon, and an air supply 
mechanism for the delivery of pressurized air to the air nozzle 
assemblies. The air supply mechanism is built into one of the rotary 
wheels around which the breaker conveyor extends. While traveling around 
this rotary wheel, the successive air nozzle assemblies are supplied with 
pressurized air from the air supply mechanism and expel the air out into 
the broken eggshells carried by the corresponding breaker assemblies 
thereby causing the residual liquid to drop into the underlying recovery 
cup assemblies. Thus the invention realizes the pneumatic residue recovery 
scheme with use of compact, economical means. 
Each air nozzle assembly includes an air nozzle movable between a retracted 
and a working position. Possibly the egg breaker assemblies may fail to 
break the shell eggs thereon. In that case the air nozzle would thrust 
into the unbroken shell egg on its movement to the working position. This 
possibility is avoided in accordance with the invention by providing a 
spring through which the air nozzle is moved from the retracted position 
to the working position. The spring yields when the air nozzle moves into 
abutment against the unbroken shell egg. 
The invention also features the improved construction of a yolk cup forming 
a part of each recovery cup assembly. Receiving both white and yolk from a 
broken egg on the overlying one of the egg breaker assemblies, the yolk 
cup causes only the white to flow out of the same and the yolk to remain 
therein. For the outflow of the white, the yolk cup has formed therein a 
recess extending downwardly from its top edge and terminating short of its 
bottom, and a slot extending at least in one circumferential direction 
from the lower end of the recess. The recess and slot are designed to 
assure ready outflow of the bodies of fluid and dense albumen contained in 
each egg. 
The above and other features and advantages of this invention and the 
manner of attaining them will become more apparent, and the invention 
itself will best be understood, from a study of the following description 
and appended claims taken together with the attached drawings.

DETAILED DESCRIPTION OF THE INVENTION 
The general organization of the exemplified high speed egg breaker in 
accordance with the invention will become apparent from a consideration of 
FIG. 1. Generally designated 1, the egg breaker comprises a conveyor 10 
extending horizontally around a plurality of, four in this embodiment, 
rotary wheels 6, 7, 8 and 9 on respective upstanding shafts 2, 3, 4 and 5. 
The conveyor 10 is composed of a pair of vertically spaced endless chains, 
as will be later explained in further detail, and will hereinafter be 
referred to as the breaker conveyor in contradistinction to other 
conveyors to be described subsequently. The breaker conveyor 10 carries a 
plurality, or multiplicity, of egg breaker assemblies 11 on its outer side 
at prescribed longitudinal spacings. 
Of the four rotary wheels supporting the breaker conveyor 10, the wheel 6 
is a sprocket wheel making positive engagement with the conveyor chains. 
The other wheels 7, 8 and 9 are all idlers serving to guide the conveyor 
chains. 
It will be observed that the breaker conveyor 10 turns right angularly 
around the sprocket wheel 6 and the idler wheel 7 which are considered to 
lie on the front side of the egg breaker 1. While the idler wheel 9 is 
spaced from the idler wheel 7 to the same extent as the spacing between 
the sprocket 6 and idler 7 wheels, the idler wheel 8 is distanced from the 
sprocket wheel 6 significantly more than the spacing between the wheels 6 
and 7 and between the wheels 7 and 9. Consequently the breaker conveyor 10 
turns acutely around the idler wheel 8 and obtusely around the idler wheel 
9. 
The trapezoid path of the breaker conveyor 10 around the four wheels 6 to 9 
arranged as above is divided into several regions for the performance of 
different egg-processing functions. They are: 
1. A loading region A, extending linearly from the idler wheel 7 to the 
sprocket wheel 6, where shell eggs E are loaded on the individual breaker 
assemblies 11 from an infeed conveyor 13 via a transfer conveyor 12. 
2. A recovery region B, extending linearly from the sprocket wheel 6 to the 
idler wheel 8 and thus shell eggs E are broken and their yolk and white 
are recovered. 
3. A residue removal region C, extending arcuately around the idler wheel 
8, where the residual liquid in the broken eggs are pneumatically removed 
therefrom and recovered. 
4. An inspection region D, extending linearly from the idler wheel 8 to the 
idler wheel 9, where the recovered egg contents are visually examined by a 
human inspector sitting on a chair 200. 
5. A discharge region F, extending arcuately around the idler wheel 7, 
where the broken egg shells as well as unbroken shell eggs, if any, are 
unloaded from the breaker assemblies 11 and discharged. 
Disposed alongs.de the loading region A, the transfer conveyor 12 performs 
the important function of efficiently loading shell eggs E on the breaker 
assemblies 11 on the breaker conveyor 10. The transfer conveyor 12 
receives the eggs to be loaded from the infeed conveyor 13. Arranged at 
right angles with respect to the transfer conveyor 12, the infeed conveyor 
13 terminates at the upstream end of the transfer conveyor. The infeed 
conveyor 13 comprises a multiplicity of transverse rows of concave rolls 
13a for holding shell eggs thereon. Although FIG. 1 shows only one 
transverse row of concave rolls 13a for simplicity, it will be understood 
that the infeed conveyor 13 can support six shell eggs in each transverse 
row in this particular embodiment. 
As illustrated in greater detail and on an enlarged scale in FIG. 2, the 
transfer conveyor 12 has an endless chain 16 extending around two sprocket 
wheels 14 and 15 rotatable about horizontal axes. Mounted on the endless 
chain 16 via respective clevises 17 are a multiplicity of concave rolls 18 
having longitudinal spacings equal to the spacings between each transverse 
row of shell eggs on the infeed conveyor 13. 
As shown on a still more enlarged scale in FIGS. 3 and 4, each concave roll 
18 of the transfer conveyor 12 is rotatable about a pin 19 extending 
parallel to the upper and lower moving parts of the endless chain 16 and 
having its opposite ends supported by the clevis 17. A drive roll 18a seen 
in FIG. 3 makes frictional contact with each concave roll 18 for imparting 
rotation thereto in the clockwise direction as viewed in this figure. The 
drive means associated with the drive rolls 18a are not shown because of 
their conventional nature. 
A U-shaped support 20 has its pair of parallel limbs 20a pivotally mounted 
on the pin 19 of each concave roll 18. Rotatably supported between these 
limbs of the U-shaped support, via a pin 22, is another concave roll 21 
which is similar in shape and size to the first recited concave roll 18. 
These two concave rolls 18 and 21, rotatable about parallel axes, make up 
a pair for conjointly holding a single shell egg E thereon in a recumbent 
attitude. The drive rolls 18a are provided adjacent to a position where 
the eggs on the infeed conveyor 13 are transported to the transfer 
conveyor 12 so that each egg on the rolls 18 and 21 is moved to a stable 
position between the pair of rolls 18 and 21 due to rotation of the rolls 
18. Both concave rolls should preferably be molded from plastics or other 
similarly pliant materials, and should be hollow, for the application of 
minimum shocks to the shell eggs as they are loaded thereon, transported 
thereby, and unloaded therefrom. 
One of the sprocket wheels 14 and 15 of the transfer conveyor 12 is coupled 
to a drive mechanism, not shown, for driving the endless chain 16. It is 
essehtial that the upper moving part of the transfer conveyor chain 16 
runs in the same direction, and at the same speed, as the breaker conveyor 
10 as it traverses the loading region A of FIG. 1. The reason for this 
will become apparent as the description progresses. 
Projecting from the free end of the pivoted support 20 carrying the concave 
roll 21 is a cam follower pin 23 resting by gravity on a cam rail 25 
secured to and extending along a guide 24 of the transfer conveyor chain 
16. The cam rail 25 is contoured to cause the pivotal motion of the 
support 20 about the pin 19 and, in consequence, the up-and-down motion of 
the concave roll 21 in relation to the associated concave roll 18. The cam 
follower pin 23 slides on a guide rail 25a fixed to a frame 201 when it 
moves along the lower moving part of the transfer conveyor chain 16. FIG. 
5 better illustrates such pivotal motion of the support 20. In a position 
opposite to the unloading end of the infeed conveyor 13, FIG. 1, the cam 
rail 25 lowers the support 20 to a position G to allow smooth loading of a 
shell egg E on each pair of concave rolls 18 and 21. As the concave roll 
pair subsequently travels through the loading region A and reaches midway 
between its opposite extremities, the cam rail 25 starts lifting the 
support 20 past its horizontal position until finally the support assumes 
the position H of FIG. 5 for the unloading of the egg from over the 
concave roll pair onto one of the egg breaker assemblies 11 on the breaker 
conveyor 10. It will be noted from FIG. 5 that the cam rail 25 is held 
sidewise against each cam follower pin 23 in the vicinity of its most 
elevated position. 
With reference to FIG. 6, a loader 26 is disposed over the loading end of 
the transfer conveyor 12 for the controlled loading of the successive 
groups of shell eggs E from the infeed conveyor 13 to the transfer 
conveyor 12. The loader 26 comprises a plurality of, four in this 
embodiment, support arms 28 mounted radially on a horizontal shaft 27, and 
loading arms 29 extending right-angularly from the outer ends of the 
support arms 28. Extending horizontally across the unloading end of the 
infeed conveyor 13, each loading arm 29 is revolved into abutment against 
one transverse row of shell eggs E being unloaded from the infeed conveyor 
13. Then the loading arm guides the group of shell eggs along a chute 30 
onto the respective pairs of concave rolls 18 and 21 of the transfer 
conveyor 12. The infeed conveyor 13 is moved intermittently by a star 
wheel 202 engaging with each roll 13a. 
The aforesaid egg breaker assemblies 11 are mounted on the breaker conveyor 
10 at spacings equal to the spacings between the pairs of concave rolls 18 
and 21 on the transfer conveyor 12. 
FIG. 7 is a detailed representation of each egg breaker assembly 11. It 
includes an egg holder 32 adapted to provide a splittable egg rest 31 on 
which a shell egg is to be placed recumbently. The egg holder 32 has a 
pair of approximately parallel arms 32a. At their ends away from the egg 
rest 31, these parallel arms 32a are respectively secured to the lower 
ends of a pair of crossing levers 35 via two plates 32b. The levers 35 are 
pivotally mounted on an upstanding mounting bracket 33 via a pin 34 
passing through their crossing point. Thus the pair of arms 32a are 
movable toward and away from each other. Sleeved upon the pin 34, a 
torsion spring 36 normally holds the arms 32a against each other. 
At their upper ends the pair of crossing levers 35 are pin jointed at 39 
and 40 to respective links 37 and 38. The link 38 is pin jointed at 41 to 
the other link 37 in its intermediate position. The link 37 carries a cam 
follower roll 42 on its end away from the pin 39. The cam follower roll 42 
is in engagement with cam means, not shown, thereby to be moved up and 
down with the travel of the egg breaker assembly 11 on the breaker 
conveyor 11. It will be seen that the levers 35 and links 37 and 38 
constitute in combination a four-bar linkage acting to cause the movement 
of the pair of holder arms 32a toward and away from each other with the 
up-and-down motion of the cam follower roll 42. The holder arms 32a are 
held separated from each other as the pivot pin 41 joining the links 37 
and 38 moves downwardly past the line connecting the pivot pins 39 and 40 
with the descent of the cam follower roll 42. 
Pivotally attached at 44 to respective holder arms 32a are a pair of egg 
breaker knives 43a which are movable with the holder arms 32a toward and 
away from each other, besides being pivotable about the axis 44. When the 
holder arms 32a are held against each other, so are the breaker knives 
43a, coacting to cut into a shell egg on the egg rest 31. The reference 
numeral 43 denotes a breaker knife assembly comprising the pair of 
separable knives 43a. The breaker knife assembly has a blade portion 43b 
movable up and down through the egg rest 31. 
Each egg breaker assembly 11 further comprises an egg retainer 45 carried 
by a retainer lever 46 having a pivot 47 mounted on the bracket 33. The 
retainer lever 46 is also operated by unshown cam means, arranged along 
the breaker conveyor 10 of FIG. 1, for pivotal motion about the pivot 47. 
Wound around the pivot 47, a torsion spring 48 biases the retainer 45 
downwardly toward the egg rest 31. A stop 49 on the bracket 33 determines 
the lower limit of the retainer 45 where it can firmly hold a shell egg 
against the rest 31. 
After being washed, shell eggs E to be processed by the apparatus of FIG. 1 
are placed on the infeed conveyor 13 and thereby transported to the 
loading end of the transfer conveyor 12. As each transverse row of shell 
eggs reach the unloading end of the infeed conveyor 13, one of the loading 
arms 29 of the loader 26 holds the eggs from below with the rotation of 
the shaft 27 in the arrow marked direction, as illustrated in FIG. 6. Then 
the loading arm 29 guides the row of shell eggs downwardly along the chute 
30 and onto the respective pairs of concave rolls 18 and 21 of the 
transfer conveyor 12. 
In this loading position of the transfer conveyor 12, the cam rail 25 holds 
the concave rolls 21 lower than the other concave rolls 18, as best seen 
in FIG. 6. Each pair of rolls 18 and 21 are thus directed toward the 
infeed conveyor 13. Accordingly the shell eggs E can be smoothly 
transferred from the infeed conveyor to the transfer conveyor via the 
chute 30 with the aid of the loader 26. It will of course be understood 
that each transverse row of shell eggs on the infeed conveyor 13 are 
loaded at one time on the transfer conveyor. 
Once loaded on the transfer conveyor 12, the shell eggs can seat stably on 
the respective pairs of rolls 18 and 21 by virtue of their concave shape. 
As has been stated, the drive rolls 18a of FIG. 3 frictionally rotate the 
concave rolls 18 as the transfer conveyor 12 transports the loaded shell 
eggs through the loading region A. This rotation of the concave rolls 18, 
combined with the vibrations of the transfer conveyor caused by the 
endless chain 16 running over the sprocket wheels 14 and 15, gradually 
causes the shell eggs to assume a recumbent attitude on the respective 
pairs of rolls 18 and 21. 
As the shell eggs travel along the loading region A as above, the cam rail 
25 gradually lifts the supports 20 carrying the concave rolls 21, causing 
these rolls to rise higher than the other concave rolls 18. Finally, when 
the concave rolls 21 reach the most elevated position H of FIG. 5, the 
shell eggs E roll under their own weight from over the pairs of concave 
rolls 18 and 21 onto the rests 31 of the corresponding breaker assemblies 
11. The pairs of concave rolls 18 and 21 on the transfer conveyor 12 and 
the egg breaker assemblies 11 on the breaker conveyor 10 travel side by 
side and at the same speed in the loading region A. Further the concave 
roll pairs and the egg breaker assemblies are at the same longitudinal 
spacings and in transverse alignment. Consequently the shell eggs E can be 
unfailingly transferred from concave roll pairs to breaker assemblies, 
there being no relative motion therebetween. 
It should be appreciated that the positions of the shell eggs on the 
concave roll pairs of the transfer conveyor 12 have been readjusted both 
by the mechanical vibrations of the conveyor and by the forced rotation of 
the concave rolls 18. All the shell eggs can thus be reloaded in the same 
recumbent attitude on the breaker assemblies. This attitude of the shell 
eggs remains unchanged on the breaker assemblies because there is no 
difference in the traveling speed of the concave roll pairs and the 
breaker assemblies as the eggs are transferred from the former to the 
latter. The correct attitude of the shell eggs on the breaker assemblies 
makes possible the proper breaking thereof in the manner to be set forth 
subsequently. It will therefore be understood that the egg breaker of this 
invention is well equipped to process eggs efficiently no matter how high 
the rate may be at which the eggs are fed into the machine. 
It is understood that the egg retainers 45 of the breaker assemblies 11 
have been raised while the shell eggs are being loaded thereon in the 
loading region A. After the loading of the eggs on the breaker assemblies, 
the retainer levers 46 are cam operated by engagement of the rear end of 
each lever 46 and a guide rail (not shown) to cause the descent of the 
retainers 45 onto the loaded eggs. The lowered retainers immovably hold 
the eggs against the rests 31. 
Immediately after the shell eggs have been clamped as above on the breaker 
assemblies 11, that is, after the breaker assemblies have turned around 
the sprocket wheel 6 into the recovery region B of FIG. 1, the breaker 
knife assembly 43 of each breaker assembly is cam-operated by engagement 
of the rear ends of the knives 43a and a guide rail 204 (FIG. 16) to cause 
its blade portion 43b to be pivoted upwardly, through the gap between the 
pair of holder arms 32a, to cut into the shell egg being caught on the 
rest 31 by the retainer 45. Then the cam follower 42 of each breaker 
assembly 11 is lowered by the unshown cam means until the pivot pin 41 
joining the links 37 and 38 of the four-bar linkage comes below the line 
between the pivot pins 39 and 40. The result is the movement of the pair 
of holder arms 32a away from each other. Thus the shell egg is broken and 
torn apart. While the broken egg shell is still caught between holder arms 
32a and retainer 45, its contents drop into a recovery cup assembly which 
is supported by the breaker conveyor 10 just under each breaker assembly 
11. 
The details of the recovery cup assemblies are yet to be studied. For the 
moment, therefore, suffice it to say that each recovery cup assembly has 
provisions for separating the white and yolk of each egg as they drop from 
the overlying breaker assembly. 
The breaking of the successive shell eggs and the recovery of the white and 
yolk therefrom take place as aforesaid in the recovery region B of the 
breaker conveyor 10. The egg contents may not be wholly recovered from the 
broken shells in the recovery region B, however. In consideration of this 
possibility, the invention suggests the provision of means for 
pneumatically removing the residual contents of the successive broken eggs 
from within the shells while they are traveling through the residue 
removal region C around the idler wheel 8. The pneumatically removed 
residues are also to drop into the recovery cup assemblies. The pneumatic 
residue removal means will be shown and described subsequently in further 
detail. 
In the succeeding inspection region D between the idler wheels 8 and 9 of 
the breaker conveyor 10, a human inspector visually inspects the recovered 
egg white and yolk in the recovery cup assemblies. If he finds that the 
recovered egg white and yolk are in an undesirable state, for example, 
where a piece of broken shell is mixed therein, he can tilt the cup 
assembly to discharge them before a recovery position for the white and 
yolk which is located between the regions D and F. Finally, in the 
discharge region F around the idler wheel 7, the broken shells as well as 
unbroken shell eggs, if any, are removed from the breaker assemblies 11 
and discharged from the machine by any known or suitable means. Thus 
unloaded, the breaker assemblies subsequently reenter the loading region 
A. The foregoing cycle of operation is repeated thereafter. 
FIGS. 8 to 10 show a slight modification of the pairs of concave rolls on 
the transfer conveyor 12 best shown in FIG. 2. The modification resides in 
a concave roll 21' of each pair, which is transversely split into two 
segments 21'A and 21'B of different axial lengths, whereas the other 
concave roll of each roll pair remains unaltered and so is designated by 
the same reference numeral 18 as in FIGS. 2 to 6. 
Also as in FIGS. 2 to 6 each concave roll 18 is rotatably mounted on the 
pin 19 supported by the clevis 17 on the endless chain 16 of the transfer 
conveyor 12. The split concave roll 21' associated with each concave roll 
is rotatably mounted on the pin 22 extending between the parallel limbs 
20a of the U-shaped support 20 pivoted on the pin 19. Projecting from the 
free end of the pivotal support 20, the cam follower pin 23 rests on the 
cam rail 25 to cause the up-and-down motion of the split concave roll 21', 
as has been explained in the foregoing. 
As will be noted upon inspection of FIGS. 8 and 9, however, the distance 
between the parallel limbs 20a of the U-shaped support 20 in relation to 
the axial dimension of the concave rolls 18 and 21' is made longer than in 
the preceding embodiment. The pair of concave rolls 18 and 21' are both 
slidable axially on the pins 19 and 22 within the limits determined by the 
parallel limbs of the U-shaped support. 
Basically the concave roll 21' may be split along a transverse plane 
anywhere between its ends. Preferably, however, the segment 21'A disposed 
forwardly with respect to the arrow marked traveling direction of the 
transfer conveyor should have an axial length approximately one third the 
total length of the concave roll. 
Before the loading of a shell egg, each pair of concave rolls 18 and 21' is 
held by inertia against the rear one of the parallel limbs 20a of the 
U-shaped support 20 with respect to the traveling direction of the 
transfer conveyor 12. The pair of concave rolls receive a shell egg from 
the infeed conveyor 13 in these positions relative to the U-shaped 
support, with the roll 21' held lower than the other 18 by the cam rail 
25, as indicated by the solid lies in FIG. 10. While being loaded, the 
shell egg first rides on the split roll 21' lying closer to the infeed 
conveyor 13. If the egg is of above-average size, it will push the segment 
21'A of the concave roll 21' away from the other segment 21'B toward the 
phantom position of FIG. 8. Thus the split roll 21' will accommodate 
itself to the size of the egg being loaded. 
As the U-shaped support 20 subsequently gains a horizontal position to hold 
the two concave rolls 18 and 21' thereon the same level, the loaded egg 
will exert a part of its weight on the other, unsplit roll 18 thereby 
causing the same to slide along the pin 19 to a position suiting the 
particular size of the egg. Then the egg will rest stably on the pair of 
concave rolls 18 and 21'. 
Upon unloading of the egg, each pair of concave rolls 18 and 21' returns to 
the solid line positions of FIG. 8 by inertia. In these positions the 
rolls are ready to receive the next egg in the loading region of the 
breaker conveyor. 
It will be understood that not one but both of each pair of concave rolls 
could be each transversely split into two segments. Also, instead of 
resorting to inertia for holding the rolls in the solid line positions of 
FIG. 8 when they are not loaded, comparatively light springs could be 
employed for the same purpose. 
Thus, according to the teachings of FIGS. 8 to 10, each pair of concave 
rolls of the transfer conveyor readily adapts himself to shell eggs of 
varying sizes. Consequently, regardless of their sizes or positions on the 
infeed conveyor, shell eggs can be stably loaded on the concave roll 
pairs, transported thereby, and unloaded therefrom onto the breaker 
assemblies. The waste of shell eggs through their falling and breaking 
during the loading on and unloading from the concave roll pairs is thus 
drastically reduced. 
FIGS. 11 to 15 are detailed representations of the aforesaid means for 
pneumatically removing or recovering the residual liquid from within the 
broken egg shells on the breaker assemblies 11 in the residue removal 
region C of the breaker conveyor 10. The residue removal means comprise an 
air nozzle assembly 52, FIGS. 11 and 12, provided for each egg breaker 
assembly 11, and an air supply mechanism 110, FIGS. 12 to 14, on the idler 
wheel 8 of the breaker conveyor 10 for the delivery of pressurized air to 
the succssive air nozzle assemblies 52 as they travel with the broken egg 
shells through the residue removal region C around the idler wheel 8. 
FIG. 11 also shows a recovery cup assembly 50 under each egg breaker 
assembly 11. Operatively mounted on the pair of vertically spaced endless 
chains 10a of the breaker conveyor 10, each associated group of egg 
breaker assembly 11, air nozzle assembly 52 and recovery cup assembly 50 
travels together through the successive processing regions A, B, C, D and 
F of FIG. 1. 
With reference to FIG. 11 in particular, a support 51 is attached to the 
outside of the pair of endless chains 10a of the breaker conveyor for 
carrying each group of egg breaker assembly 11, recovery cup assembly 50 
and air nozzle assembly 52. A mount 53 overlies each support 51 for 
pivotal motion about an axis at 51a. As will be seen also from FIG. 12, 
this axis extends approximately tangent to the idler wheel 8 when the pair 
of breaker conveyor chains are traveling in engagement with the pair of 
concentric discs 94 of the idler wheel driven by a driving means 205 (FIG. 
12). The pivotal mount 53 supports one air nozzle assembly 52 and one egg 
breaker assembly 11 thereon. 
The representative air nozzle assembly 52 of FIG. 11 includes a guide rod 
54 immovably supported on the pivotal mount 53 so as to extend radially of 
the idler wheel 8 when the breaker conveyor chains 10a are traveling 
around the same. Extending parallel to the guide rod 54 is an elongate air 
nozzle 56 supported at its front or right hand end by an upstanding 
portion 53a of the pivotal mount 53 for longitudinal sliding motion 
therethrough. The rear end of the air nozzle 56, on the other hand, is 
slidably received in a sleeve 55a rigidly connected to a slide 55 slidably 
fitted over the guide rod 54. A pin 56a on the air nozzle 56 prevents the 
detachment of the sleeve 55a from over the air nozzle 56. Sleeved upon the 
air nozzle 56, a compression spring 61 acts between the sleeve 55a and a 
collar 63 fixedly mounted on the air nozzle, normally holding the sleeve 
on the rear end of the air nozzle. 
Another compression spring 64 around the guide rod 54 extends between mount 
portion 53a and slide 55, holding the latter in abutment against a cam 
rail 62 on a stationary part, not shown, of the egg breaker. The cam rail 
62 is contoured to cause the movement of the slide 55 back and forth along 
the guide rod 54. 
Normally, or when the air nozzle assembly 52 is not in the residue removal 
region C of FIG. 1, the cam rail 62 holds the slide 55 in the position of 
FIG. 11 under the bias of the compression spring 64. The sleeve 55a 
connected to the slide 55 holds the air nozzle 56 in a retracted position 
as shown in FIG. 11. When the air nozzle assembly 52 comes to the residue 
removal region, the cam rail 62 causes the slide 55 to travel forwardly 
along the guide rod 54 against the bias of the compression spring 64. 
Moving with the slide 55, the sleeve 55a acts on the air nozzle 56 via the 
compression spring 61 thereby thrusting the air nozzle forwardly of the 
mount 53 to an extended working position. 
As shown in both FIGS. 11 and 12, the egg breaker assembly 11 is mounted 
over the air nozzle assembly 52, with its egg rest disposed forwardly of 
the air nozzle assembly. The air nozzle 56 on extension has its front end 
positioned between the broken egg shells Eb, FIG. 15, being carried by the 
egg breaker assembly 11. It will also be noted from FIG. 15 that the air 
nozzle 56 has a pair of air outlet ports 57 on opposite sides of its front 
end portion. These outlet ports are oriented slightly upwardly for 
directing air under pressure into the deepest parts of the broken egg 
shells Eb. 
With reference again to FIG. 11, the air nozzle 56 has an air passageway 58 
formed axially therein for communicating the pair of air outlets 57 with a 
flexible conduit 60 leading to an air passageway 59a in the guide rod 54. 
The air passageway 59a communicates with an outlet port 59b in a coupling 
59 rigidly mounted on the rear end of the pivotal mount 53. The coupling 
59 has a downwardly open, countersunk inlet port 65 for placing the air 
nozzle 56 in and out of communication with the air supply mechanism 110, 
FIGS. 12 to 14, in a manner yet to be described. A valve actuator rod 99, 
embedded in the coupling 59, projects out of the inlet port 65. 
A cam follower 92 projects rearwardly from the coupling 59 and is movably 
caught between a pair of cam rails 93. These cam means coact to cause the 
pivotal motion of the mount 53, together with the egg breaker assembly 11 
and air nozzle assembly 52 thereon, about the horizontal axis at 51a. This 
pivotal motion of the mount 53 is necessary for the desired mechanical 
connection and disconnection of the coupling 59 to and from the air supply 
mechanism 110. 
Reference is now directed to FIGS. 12 to 14 in order to describe the air 
supply mechanism 110 in detail. The air supply mechanism includes the 
idler wheel 8 having the pair of discs 94 rigidly mounted on the 
upstanding rotary shaft 4 for engagement with the respective endless 
chains 10a of the breaker conveyor. The idler wheel shaft 4 has an air 
passageway 75 formed axially therethrough for communication with a source 
of air under pressure. 
Airtightly mounted on the idler wheel 8 is a disclike air distributor 95 
which is concentric with the idler wheel and which has a diameter less 
than that of the idler wheel. The air distributor 95 has a plenum chamber 
96 formed centrally therein in constant communication with the air 
passageway 75 in the idler wheel shaft 4. A plurality of branch 
passageways 97 extend radially outwardly from the plenum chamber 96 and 
terminate just short of the periphery of the air distributor 95. At the 
outer ends of the branch passageways 97 there are valve chambers 98, FIG. 
14, housing valve members 111 and opening upwardly. Air-tightly engaged in 
the upward openings of the valve chambers are hollow male couplings 66 of 
annular arrangement for selective mating engagement with the coupling 59 
of each air nozzle assembly 52. The coupling 59 of each air nozzle 
assembly will hereinafter be referred to as the female coupling in 
contradistinction to the male couplings 66 of the air supply mechanism 
110. Each male coupling 66 has a frustoconical portion 66a projecting 
upwardly of the air distributor 95 to fit in the countersunk inlet port 65 
of the female coupling 59. 
Movable up and down in each valve chamber 98, the valve member 111 is 
biased upwardly by a spring 300 to normally butt on the bottom of the male 
coupling 66 and hence to close the air outlet therein. Upon engagement of 
the female coupling 59 of each air nozzle assembly 52 with any one male 
coupling 66 of the air supply mechanism 110 as in FIGS. 12 and 14, the 
valve actuator rod 99 depresses the valve member 111 against the force of 
the spring 300, thereby causing the flow of pressurized air from air 
supply mechanism to air nozzle assembly. 
A pressure meter 101, FIGS. 12 to 14, is mounted on the air distributor 95 
in air communication with the plenum chamber 96. The pressure meter 
visually indicates the pressure of the air being delivered from air supply 
mechanism 110 to successive air nozzle assemblies 52. 
Each recovery cup assembly 50 is shown in FIG. 11 as comprising a yolk cup 
81 and an albumen cup 82 for separately recovering the yolk and white of 
an egg as it is broken by the overlying breaker assembly 11. The yolk cup 
81 receives both yolk and white from the broken egg and causes only the 
white to flow out of a recess 86 down into the underlying albumen cup 82. 
Some preferred forms of the yolk cup in accordance with the invention will 
be disclosed later. 
Both yolk cup 81 and albumen cup 82 are mounted on the support 51 via links 
84 and 85 for joint pivotal motion about a horizontal axis. The albumen 
cup 82 has a cam follower 82a projecting forwardly therefrom to rest on a 
cam rail 87 extending along the path of the breaker conveyor 10. The cam 
rail 87 causes the recovery cup assembly 50 to tilt forwardly for the 
discharge of the recovered yolk and white onto respective chutes or 
receptacles in the region between the wheels 9 and 7 (FIG. 1). After this 
discharge, the recovery cup assembly 50 is washed for the next process by 
a proper means (not shown). 
The following is the description of operation of the air nozzle assemblies 
52 and air supply mechanism 110 constructed as in FIGS. 11 to 14. As each 
air nozzle assembly 52 approaches or enters the residue removal region C, 
FIG. 1, around the idler wheel 8, the cam rail causes the slide 55 to 
travel forwardly along the guide rod 54 against the bias of the 
compression spring 64. The sleeve 55a travels forwardly with the slide 55 
and so acts on the compression spring 61 to cause the forward movement of 
the air nozzle 56 therethrough. The forward travel of the air nozzle 56 
terminates when its front end becomes positioned between the two fractured 
pieces of the eggshell Eb being carried by the breaker assembly 11 
associated with the air nozzle assembly 52. 
Possibly the shell egg on the breaker assembly may have not been broken in 
the recovery region B for some reason or other. Then the air nozzle 56 on 
movement toward its working positon will hit the shell egg but will not 
thrust into it because then the compression spring 61 will yield to 
prevent the continued forward travel of the air nozzle despite the full 
forward movement of the slide 55 with the sleeve 55a. 
Immediately after the travel of the air nozzle 56 to its working position, 
or when the air nozzle assembly 52 enters the residue removal region C, 
the pair of cam rails 93 at its rear end causes the pivotal mount 53 to 
pivot counterclockwise, as viewed in FIGS. 11, 12 and 14, until the female 
coupling 59 of the air nozzle assembly becomes engaged with one of the 
male couplings 66 of the air supply mechanism 110 on the idler wheel 8. As 
the frustoconical portion 66a of the male coupling airtightly fits in the 
countersunk inlet port 65 of the female coupling 59, the valve actuator 
rod 99 projecting downwardly from the latter depresses the valve member 
111 against the bias of the spring 300. Thereupon air under pressure flows 
from passageway 75 in the idler wheel shaft 4 to air nozzle 56 via plenum 
chamber 96, one of the branch passageways 97, one of the valve chambers 
98, one of the male couplings 66, female coupling 59, passageway 59a in 
the guide rod 54, and flexible conduit 60. 
The air nozzle 56 expels the pressurized air out of the two ports 57 formed 
in approximately diametrically opposite positions in its front end. As has 
been stated, these outlet ports are directed slightly upwardly, so that 
the air streams issuing therefrom are applied to the deepest parts of the 
broken eggshell pieces Eb on the breaker assembly 11, as illustrated in 
FIG. 15. 
Ideally, all the contents of the eggs are recovered from the broken shells 
in the recovery region B. However, depending upon the way each shell egg 
is cut and fractured, a part of the white or a fraction of the yolk that 
has been severed by the breaker knife assembly may remain in the broken 
eggshell. All such residual liquid is blown out of the eggshell fragments 
by the forced streams of air from the air nozzle 56, falling into the yolk 
cup 81. The white will overflow from the yolk cup 81 through its recess 86 
and fall further down into the albumen cup 82. 
The same residue recovery operation is performed for the successive 
combinations of egg breaker assemblies 11, recovery cup assemblies 50, and 
air nozzle assemblies 52 as they travel with the breaker conveyor 10 
through the residue removal region C around the idler wheel 8. 
About the moment when each group of egg breaker assembly, recovery cup 
assembly and air nozzle assembly leaves the residue removal region C, the 
pair of cam rails 93 lifts the pivotal mount 53 about its axis 51a thereby 
causing disengagement of the female coupling 59 from one of the male 
couplings 66 on the idler wheel 8. The group of three assemblies in 
question can now travel away from the idler wheel 8. Upon disengagement 
from the female coupling 59, the male coupling 66 has its air outlet 
reclosed by the valve member 111 under the bias of the spring 300. The cam 
rail 62 causes the slide 55 to travel rearwardly along the guide rod 54 
under the effect of the compression spring 64 and thus allows the air 
nozzle 56 to return to the illustrated retracted position. 
It will be appreciated that the residue removal means set forth in the 
foregoing are well calculated to make possible the complete recovery of 
the liquid from each broken egg, with provisions for preventing the air 
nozzle from thrusting into an unbroken shell egg and so wasting it. 
Particular attention is called to the fact that the air supply mechanism 
110 is built into the idler wheel 8 and cooperates with the air nozzle 
assemblies 52 traveling with the respective egg breaker assemblies 11 on 
the breaker conveyor 10. Thus the residue removal means require no 
particular installation space but can efficiently remove the residual 
liquid from within the broken eggshells on the running breaker conveyor. 
As an additional advantage, the air nozzle assemblies can be exactly 
positioned in relation to the air supply mechanism as the former are 
mounted on the breaker conveyor chains running in engagement with the 
idler wheel incorporating the air supply mechanism. 
As has been stated in connection with FIG. 1, the broken eggshells as well 
as unbroken shell eggs are unloaded from the breaker assemblies 11 in the 
discharge region F around the idler wheel 7. The nozzle assemblies 52 may 
be used, without the aid of the air supply mechanism 110, for the 
unloading of the broken eggshells and unbroken shell eggs from the breaker 
assemblies in the discharge region. 
FIG. 16 shows a modified air nozzle assembly 52', for combined use with a 
correspondingly modified air supply mechanism 110' of FIG. 17. As in the 
preceding embodiment, the air nozzle assembly 52' is provided, together 
with the associated one of the egg breaker assemblies 11, on a mount 53 
pivoted at 51a on a support 51 carried by the pair of endless chains 10a 
of the breaker conveyor. The recovery cup assembly 50 is also carried by 
the support 51 under the egg breaker assembly 11. 
The modified air nozzle assembly 52' is analogous in construction to the 
air nozzle assembly 52 of FIGS. 11 and 12 except for the arrangement of 
its constituent parts. Included is a guide rod 54 fixedly mounted on the 
pivotal mount 53 so as to extend normally to the pair of breaker conveyor 
chains 10a, or radially of the idler wheel 8 when the breaker conveyor 
chains are traveling around the same. A slide 55 is slidably mounted on 
the guide rod 54 and is normally held in the illustrated position on the 
rear end of the guide rod by a compression spring 64. 
Arranged parallel to the guide rod 54 and disposed thereunder, an elongate 
air nozzle 56 is slidably supported at its opposite ends by the pivotal 
mount 53 and by a member 55a substantially integral with the slide 55 on 
the guide rod 54. A compression spring 61 around the air nozzle 56 extends 
between the member 55a and a collar 63 on the air nozzle to transmit the 
motion of the slide 55 to the air nozzle therethrough. A rear end 
enlargement 56a of the air nozzle 56 prevents its detachment from the 
member 55a. 
In sliding engagement with the member 55a integral with the slide 55 is a 
cam rail 62 for causing the travel of the slide back and forth along the 
guide rod 54. Upon forward or rightward travel of the slide 55 against the 
force of the compression spring 64, the member 55a acts on the other 
compression spring 61 thereby causing the air nozzle 56 to travel in the 
same direction toward the egg breaker assembly 11. The cam rail 62 
normally holds the air nozzle 56 in the illustrated position. 
The air nozzle 56 has a pair of air outlet ports 57 formed in approximately 
diametrically opposite positions in the adjacency of its front end, as in 
FIG. 15. Also as in the preceding embodiment, these air outlet ports are 
oriented slightly upwardly for directing the streams of pressurized air 
into the deepest parts of the broken eggshells Eb on the breaker assembly 
11. 
The pair of air outlet ports 57 of the air nozzle 56 communicate via a 
passageway 58 therein with a flexible conduit 60 leading to a female 
coupling 59 rigidly mounted atop the pivotal mount 53. The female coupling 
59 has an upwardly open, countersunk inlet port 65 for placing the air 
nozzle 56 in and out of communication with the air supply mechanism 110' 
of FIG. 17. 
Although the air nozzle assembly 52' is pivotable with the mount 53 about 
the axis 51a as in the FIGS. 11 to 14 embodiment, the pivoting of the air 
nozzle assembly 52' is intended to make possible the optimum positioning 
of the front end of the air nozzle 56 between the broken eggshell pieces 
on the breaker assembly 11. The necessary motion for the connection and 
disconnection of the air nozzle assembly to and from the air supply 
mechanism 110' is performed on the side of the air supply mechanism, as 
will be understood from the following description of FIG. 17. 
The air supply mechanism 110' comprises a plurality of pivotal arms 69 on 
respective brackets 68 extending radially from the upstanding shaft 4 of 
the idler wheel 8. The single pivotal arm 69 seen in FIG. 17 is typical of 
all such arms bracketed to the idler wheel shaft 4. The representative arm 
69 is medially pivoted at 70 on one bracket 68, for pivotal motion about 
the horizontal axis 70, and generally extends radially of the idler wheel 
shaft 4. 
Projecting from the outer end of the pivotal arm 69 is a conduit 80 which 
is bent downwardly to terminate in a male coupling 66 for delivering 
pressurized air to the air nozzle assembly 52'. The male coupling 66 is 
movable into and out of airtight engagement with the female coupling 59 of 
the air nozzle assembly 52' with the pivotal motion of the arm 69 about 
the axis 70. Preferably the conduit 80 has some resiliency so that the 
male coupling 66 may fit closely in the countersunk inlet port 65 of the 
female coupling 59 with a minimum of shock. 
It will now be seen that the illustrated and other pivotal arms 69 together 
with the male couplings 66 are arranged at constant angular spacings about 
the idler wheel shaft 4. The angular spacings therebetween correspond to 
the angular spacings between the air nozzle assemblies 52' on the breaker 
conveyor chains 10a traveling around the idler wheel 8. Thus the male 
couplings 66 of the air supply mechanism 110' can be moved into and out of 
engagement with the female couplings 59 of the successive air nozzle 
assemblies 52' with the pivotal motion of the arms 69 in a controlled 
sequence. 
Adapted for such controlled pivotal motion of the arms 69 is a cam rail 71 
immovably supported around the idler wheel shaft 4 for engagement with a 
cam follower 72 rotatably mounted on the inner end of each arm 69. When 
pivoted from the solid-line to phantom position in FIG. 17, each arm 69 
has its male coupling 66 engaged in the female coupling 59 of one of the 
air nozzle assemblies 52'. 
The conduit 80 carrying each male coupling 66 communicates by way of a 
conduit 79 with the outlet port 73b of an on-off valve 73 fixedly mounted 
on each bracket 68. The inlet port 73a of this on-off valve communicates 
by way of a conduit 76 with the air passageway 75 formed axially in the 
idler wheel shaft 4. The passageway 75 communicates with a source 78 of 
air under pressure via a rotary valve 77 at the bottom end of the idler 
wheel shaft 4 rotatably supported by a bearing 203. 
Normally held closed, the on-off valve 73 must be opened when the male 
coupling 66 is in engagement with the female coupling 59 of the air nozzle 
assembly 52' in the residue removal region C. To this end the on-off valve 
73 has a valve actuator 74 extending downwardly therefrom into abutment 
against the pivotal arm 69. Thus the on-off valve 73 is opened upon 
pivotal motion of the arm 69 to the phantom position by the effect of the 
cam rail 71. 
The recovery cup assembly 50, FIG. 16, for use with each modified air 
nozzle assembly 52' can be similar in construction to the recovery cup 
assembly of FIG. 11, comprising the recessed yolk cup 81 immediately 
underlying the egg breaker assembly 11, and the larger albumen cup 82 
below the yolk cup. Means for mounting these cups on the pair of breaker 
conveyor chains 10a, however, differ from those of FIG. 11. 
The cup-mounting means of FIG. 16 include three pivoted links 83, 84 and 85 
on the support 51 adapted to allow the tilting motion of the cups 81 and 
82 as dictated by the cam rail 87 on which rests the cam follower 82a 
projecting from the free end of the albumen cup 82. Besides being 
pivotable with the albumen cup 82, the yolk cup 81 is tiltable about a pin 
88 supporting the yolk cup on the link 85. The pin 88 extends horizontally 
in a direction normal to the breaker conveyor chains 10a, so that the yolk 
cup can be tilted toward its side where the recess 86 is formed. Parallel 
to the pin 88, another pin 89 is secured to the yolk cup 81 and engaged in 
an arcuate slot 90 in the link 85 in order to limit the angle through 
which the yolk cup is pivoted about the pin 88. Normally the yolk cup 81 
is held horizontally by a torsion spring 91. The pin 89 is cam-operated to 
tilt the yolk cup 81 against the force of the spring 91 when the white and 
yolk drops from the broken shell egg being carried by the overlying 
breaker assembly 11. Such tilting of the yolk cup 81 is of course intended 
to expedite the outflow of the white through the recess 86. 
In the operation of each air nozzle assembly 52' of FIG. 16 and the air 
supply mechanism 110' of FIG. 17, the cam rail 62 causes the slide 55 of 
the air nozzle assembly to travel forwardly along the guide rod 54 against 
the force of the compression spring 64. Traveling with the slide 55, the 
member 55a acts on the air nozzle 56 via the compression spring 61 thereby 
causing the air nozzle to move to its working position where its front end 
lies between the severed fragments of the eggshell Eb on the breaker 
assembly 11 as in FIG. 15. If the shell egg has not been broken in the 
recovery region B, the compression spring 61 will yield when the air 
nozzle 56 hits the shell egg, as in the air nozzle assembly of FIGS. 11 
and 12. 
Also, when the air nozzle assembly 52' in question enters the residue 
removal region C, the cam rail 71 of the air supply mechanism 110' on the 
idler wheel 8 causes one of the arms 69 to pivot to the phantom position 
of FIG. 17. Thereupon the male coupling 66 carried by this pivoted arm 69 
airtightly fits in the countersunk inlet port 65 of the female coupling 59 
of the air nozzle assembly 52'. 
The pivotal motion of the arm 69 also results in the activation of the 
valve actuator 74 of the on-off valve 73. With the on-off valve thus 
opened, the pressurized air flows from its source 78 to the male coupling 
66 by way of the rotary valve 77, passageway 75 in the idler wheel shaft 
4, conduit 76, on-off valve 73, and conduits 79 and 80. The pressurized 
air flows from the male coupling 66 into the female coupling 59 and thence 
into the air nozzle 56 of the air nozzle assembly 52' by way of the 
flexible conduit 60. 
The manner in which the pressurized air is expelled from the air nozzle 56 
into the broken eggshell on the breaker assembly 11 for the removal of the 
residual liquid therefrom is as set forth above in connection with FIGS. 
11 to 15. The advantages gained by this modified air nozzle assemblies 52' 
and air supply mechanism 110' will also be apparent from the foregoing. 
FIGS. 18 to 22 illustrate preferred forms of the yolk cup 81 seen in FIGS. 
11 and 16. With particular reference to FIGS. 18 and 19, the exemplified 
yolk cup 81 has an upper portion 81c rather gently tapering downwardly, 
and a lower portion 81b tapering at a greater angle to a flat bottom 81d 
sized to allow the yolk Ea to rest neatly thereon. 
The noted recess 86 extends downwardly from the top edge 81a of the yolk 
cup to a level slightly below the top of the egg yolk Ea to be received 
therein. This recess is defined by three pairs of opposed linear edges 
86c, 86d and 86e as indicated in FIG. 19. The uppermost pair of edges 86c 
upwardly diverge apart at an angle of, for example, 90 degrees. The 
intermediate pair of edges 86d also upwardly diverge apart, but at a 
smaller angle. The lowermost pair of edges 86e are parallel to each other. 
In short the edges bounding the recess 86 diverge apart at progressively 
greater angles as they extend upwardly, thereby providing two pairs of 
angles 86a and 86b. This shape of the recess 86 is intended to facilitate 
the separation of the egg white in the initial stage of its outflow, as 
will be later explained in further detail. 
Extending circumferentially from the lower end of the recess 86 is a slot 
100 having a length approximately one sixth the cup circumference for the 
best results. As shown in an enlarged vertical section in FIG. 22, the 
slot 100 lies in the tapering lower portion 81b of the yolk cup, with its 
lower edge 100a disposed slightly below the top of the yolk Ea on the 
bottom of the cup. 
In the yolk cup 81 shown in FIGS. 18, 19 and 21, the slot 100 extends in 
the direction in which the cup is tilted for the discharge of the yolk 
therefrom. Alternatively, as depicted in FIG. 20A, the slot 100 may extend 
in opposite circumferential directions from the lower end of the recess 86 
to the same extent. Further the slot 100 need not be of constant width as 
in the two examples disclosed above. Thus, in the additional example given 
in FIG. 20B, the slot 100 extending in one circumferential direction from 
the lower end of the recess 86 has an upper edge 100b sloping downwardly 
as it extends away from the recess 86. FIG. 20C illustrates a further 
example wherein the slot 100 extending in opposite circumferential 
directions from the lower end of the recess 86 has upper edges 100b 
sloping downwardly as they extend away from the recess. 
As a shell egg is broken and severed by each breaker assembly in the above 
described manner, its contents fall into the underlying yolk cup 81. 
Having a greater specific gravity than the white, the yolk seats directly 
on the flat bottom 81d of the yolk cup 81, with the white overlying it. 
The white of an egg consists of an outer body of fluid albumen and an inner 
mass of dense albumen. The fluid albumen encloses the dense albumen, which 
in turn surrounds the yolk. The fluid albumen first flows out of the 
divergent recess 86 in the yolk cup 81, followed by the escape of the 
dense albumen through the horizontal slot 100. In thus escaping out of the 
slot 100, the dense albumen will first hang from the cup, throughout the 
slot, but then will be cut off by its elongate lower edge 100a. 
As has been mentioned in conjunction with FIG. 16, the yolk cup 81 can be 
tilted or oscillated about its supporting pin 88 by the cam-operated pin 
89 between the horizontal position and a tilted position where its 
recessed side is lowered. The repeated tilting of the yolk cup is 
especially effective for fresh eggs whose white and yolk stick firmly 
together. The fluid albumen of a fresh egg will protrude from the 
divergent recess 86 upon initial tilting of the yolk cup 81. During the 
subsequent return of the yolk cup to the horizontal position, the 
divergent recess 86 with its angles 86a and 86b will hamper the inflow of 
the fluid albumen back into the cup. The dense albumen, on the other hand, 
will hang out of the horizontally elongated slot 100 in the form of a 
flat, thin body upon tilting of the yolk cup. Thus, by the repeated 
tilting of the yolk cup, the white will separate from the yolk and drop 
into the albumen cup 82 of FIG. 11 or 16. 
Upon completion of the repeated tilting of the yolk cup 81 by the unshown 
cam with the lapse of a preassigned length of time, the yolk cup will 
return to the horizontal position by the effect of the torsion spring 91. 
Then, in the predetermined region between the regions D and F along the 
breaker conveyor 10, FIG. 1, the yolk cup 81 is tilted forwardly, or 
toward the right as viewed in FIGS. 18 to 21, thereby causing the 
recovered yolk to flow out over its brim 81a. 
The foregoing will have made clear that the various examples of the yolk 
cup in accordance with the invention are well calculated to realize the 
ready and positive separation of the white and yolk regardless of whether 
the eggs being processed are fresh or not. Thus, despite the high speed 
processing of eggs for which the invention is intended, the recovered yolk 
will be nearly completely free from the white. 
It should also be noted that the recess 86 with the slot 100 is situated on 
the trailing side of each yolk cup with respect to its traveling direction 
on the breaker conveyor. Thus positioned, the recess presents no 
possibility of breaking the membrane enveloping the yolk during its 
discharge from the tilted yolk cup. The breaking of the vitellin membrane 
is objectionable since the yolk will then become loose and spread over the 
cup and other parts, necessitating their cleaning. 
The fact that the slot 100 in each yolk cup extends from the lower end of 
the recess 86 in a direction away from the breaker conveyor chains is also 
an important factor for the efficient separation of the white and yolk. As 
the breaker conveyor turns around one of the idler wheels, the dense 
albumen protruding from the slot 100 will be centrifugally thrown away 
from the cup and so will separate from the yolk. 
Furthermore, as shown in FIG. 2, the drive roll 18a is made of rubber and 
is rotated by a belt 300a. It extends through a predetermined length. The 
drive roll 18a does not extend to a position P1 where each shell egg is 
transferred from the infeed conveyor 13 to the transfer conveyor 11. 
However, the right end of the roll 18a extends to a position P2 where the 
egg shell are transferred from the transfer conveyor 11 to the breaker 
assembly as shown in FIG. 5. Each shell egg is rotated around its axis in 
a direction where it is easily moved toward the breaker assembly 
(counterclockwise direction as viewed in FIG. 5), whereby the shell egg is 
smoothly transferred from the transfer conveyor 12 to the breaker assembly 
11 when the concave rolls 21 reach the most elevated position H. The drive 
roll 18a tapers at its left end 18b, as viewed in FIG. 2, so that each 
concave roll 18 can come into smooth contact with the drive roll 18a. 
While the present invention has been shown and described in terms of but 
one embodiment and modifications thereof, it is recognized that departures 
may be made therefrom within the scope of the invention, which is not to 
be limited to the details disclosed herein but is to be accorded the full 
scope of the claims so as to embrace any and all equivalent processes and 
devices.